EP0912382B1 - Power-assisted braking device with a variable assistance ratio - Google Patents

Power-assisted braking device with a variable assistance ratio Download PDF

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Publication number
EP0912382B1
EP0912382B1 EP97924090A EP97924090A EP0912382B1 EP 0912382 B1 EP0912382 B1 EP 0912382B1 EP 97924090 A EP97924090 A EP 97924090A EP 97924090 A EP97924090 A EP 97924090A EP 0912382 B1 EP0912382 B1 EP 0912382B1
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EP
European Patent Office
Prior art keywords
hydraulic piston
master cylinder
braking device
opening
way valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP97924090A
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German (de)
French (fr)
Other versions
EP0912382A1 (en
Inventor
Jean-Pierre Gautier
Ulysse Verbo
Fernando Sacristan
Juan Simon Bacardit
Jean-Marc Attard
Stéphane LACROIX
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bosch Systemes de Freinage SAS
Original Assignee
Bosch Systemes de Freinage SAS
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Publication of EP0912382A1 publication Critical patent/EP0912382A1/en
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
    • B60T13/24—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being gaseous
    • B60T13/46—Vacuum systems
    • B60T13/52—Vacuum systems indirect, i.e. vacuum booster units
    • B60T13/57—Vacuum systems indirect, i.e. vacuum booster units characterised by constructional features of control valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
    • B60T13/24—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being gaseous
    • B60T13/46—Vacuum systems
    • B60T13/52—Vacuum systems indirect, i.e. vacuum booster units
    • B60T13/565—Vacuum systems indirect, i.e. vacuum booster units characterised by being associated with master cylinders, e.g. integrally formed
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
    • B60T13/24—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release the fluid being gaseous
    • B60T13/46—Vacuum systems
    • B60T13/52—Vacuum systems indirect, i.e. vacuum booster units
    • B60T13/573—Vacuum systems indirect, i.e. vacuum booster units characterised by reaction devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T11/00—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant
    • B60T11/10—Transmitting braking action from initiating means to ultimate brake actuator without power assistance or drive or where such assistance or drive is irrelevant transmitting by fluid means, e.g. hydraulic
    • B60T11/16—Master control, e.g. master cylinders
    • B60T11/236—Piston sealing arrangements

Definitions

  • the present invention relates to assisted braking devices for motor vehicles, comprising a master cylinder controlling the hydraulic pressure in the braking circuit connected to the vehicle brakes, this master cylinder being capable of being actuated by a servomotor assistance tire when the vehicle driver presses the brake pedal braking.
  • the master cylinder is filled with a freming fluid and fitted with a piston main hydraulics for receiving an actuating force consisting of a force input and assistance force both acting in an axial direction.
  • the pneumatic booster can be controlled by application of the input force on a control rod controlling the opening of a valve, to exert the actuating force on the main hydraulic piston of the master cylinder,
  • the servomotor comprising a rigid casing separated in a sealed manner into two chambers at by means of a movable partition capable of being stressed by a pressure difference between the two chambers resulting from the opening of the valve and driving a mobile pneumatic piston relative to the casing and carrying the valve, the input force being transmitted through a reaction disc on which the pneumatic piston also rests for him provide at least some of the assist force.
  • a device of this type is well known in the prior art and is for example described in US-A-4,491,058.
  • braking devices have the advantage, resulting from the use of a piston pneumatic movable with respect to the rigid casing, that the total stroke available for the control rod, therefore for the brake pedal, is relatively long, which constitutes a necessary condition to ensure optimal control of the vehicle deceleration when braking.
  • Braking systems were then developed comprising various sensors sensitive to the force applied to the brake pedal and / or at the speed of application of this force to correct, by means of a pneumatic solenoid valve controlled by a receiving microprocessor the signals from these sensors, the pressure difference prevailing in the actuator to make it increase faster, so as to also increase the assistance force faster and therefore correct the lengthening of the servomotor response time by an increase in the assistance force.
  • the mechanical components on which the sensors are installed have an inertia or a time relatively large response, so that the electronic correction system does not come into game only after a relatively long time after the detection of the emergency.
  • assisted braking devices have been developed in which the reaction acting on the control rod is no longer mechanically supplied by a reaction disk, but by the hydraulic pressure prevailing in the master cylinder.
  • the main hydraulic piston of the master cylinder itself comprises a hollow mobile cylinder, communicating with the master cylinder, receiving at least part of the assistance force, and inside which slides, tightly and in the direction axial, a secondary hydraulic piston capable of receiving at least the input force, elastic means exerting an elastic force between the secondary hydraulic piston and the cylinder movable and urging the secondary hydraulic piston towards the master cylinder, at at least one opening being made in the movable cylinder to communicate the interior of the latter with the interior of the master cylinder.
  • Such a device is for example described in document FR-A-2 658 466.
  • the present invention provides an assisted braking device for a vehicle with engine, comprising on the one hand a master cylinder filled with a brake fluid and equipped with a main hydraulic piston intended to receive an actuating force consisting of a input force and assistance force both acting in an axial direction, and on the other hand a pneumatic assistance servomotor capable of being controlled by application of the input force on a control rod secured to a plunger controlling the opening a three-way valve, to exert the actuating force on the hydraulic piston main, the actuator having a rigid envelope separated in a sealed manner at at least two rooms by means of at least one movable partition, capable of being requested by a pressure difference between the two chambers resulting from the opening of the three-way valve tracks and drive a pneumatic piston, movable relative to the casing, carrying the valve to three ways and contributing at least to transmit the assistance force, the hydraulic piston main of the master cylinder itself comprising a mobile, hollow, communicating cylinder with the interior volume of the master cylinder, receiving at least part of the assistance force, the
  • the secondary hydraulic piston comprising a normally open two-way valve means capable of interrupting the communication between the interior volume of the master cylinder and the interior of the movable cylinder.
  • Such an assisted braking device is for example known from document EP-B-0 662 894.
  • the secondary hydraulic piston is composite, and comprises a first part in abutment, in the rest position, against the movable cylinder under the effect of the first elastic means, and a second part capable of sliding relative to the first part, second elastic means exerting a second elastic force towards the rear on the second part to urge it into abutment, in the rest position, against the first part.
  • the first and second parts of the secondary hydraulic piston can slide relative to each other and actuate the two-way valve means in the closing direction, so that the hydraulic piston secondary receives the internal pressure reaction of the master cylinder only on a section lower than that on which it receives this pressure reaction during braking in emergency conditions, from which it follows that the assistance report of the assisted braking device is greater in emergency braking than that obtained for braking under conditions normal.
  • a system of this type comprises a servomotor 100 and a master cylinder 200.
  • the servomotor 100 is designed to be fixed in the usual way to an apron (not shown) of separation between an engine compartment of a vehicle and the passenger compartment of this vehicle and for be actuated by a brake pedal (not shown) located in this passenger compartment.
  • the master cylinder 200 controlling the hydraulic brake system of the vehicle is fixed on the wall front of actuator 100.
  • the part of this servomotor / master cylinder assembly is called “front” last turned towards the master cylinder 200 and “rear” of this assembly, the part facing the brake pedal 12. In the Figures, the front is thus on the left and the rear on the right.
  • the servomotor 100 itself comprises a rigid envelope whose internal volume is separated into a front chamber 12 and a rear chamber 14, in leaktight fashion, by a partition mobile 16 comprising a membrane 18 and a rigid skirt 20 and capable of causing a pneumatic piston 22 movable inside the casing 10.
  • the front chamber 12 the front face of which is closed in a sealed manner by the master cylinder 200, is permanently connected to a vacuum source (not shown) through a connection 15.
  • the pressure in the rear chamber 14 is controlled by a three-way valve 24, controlled by a control rod 26 connected to the brake pedal and secured to a plunger 28.
  • valve 24 When the control rod 26 is in the rest position, that is to say pulled to the right, the valve 24 establishes communication between the two chambers 12 and 14 of the actuator. The rear chamber 14 then being subjected to the same vacuum as the front chamber 12, the piston 22 is pushed to the right, in the rest position, by a spring 25.
  • control rod 26 The actuation of the control rod 26 to the left has the effect, at first, move valve 24 so that it isolates chambers 12 and 14 from each other, then in a second time, to move this valve so that it opens the rear chamber 14 under pressure atmospheric.
  • the braking force exerted on the control rod 26, or "input force” and the assistance force during braking, or “assistance force”, resulting from the thrust of the movable partition 16, are then, applied together along the axis XX 'of the servomotor 100 in the direction of the master cylinder 200, and combine to constitute the actuating force of the latter.
  • the actuating force is applied to the main hydraulic piston 30 of the master cylinder and causes it to move to the left (in the Figures), which causes an increase in the pressure of the brake fluid present in the interior volume V of the master cylinder 200, and a brake actuation (not shown) connected to the latter
  • the main hydraulic piston 30 is in fact composite and comprises on the one hand a movable and hollow cylinder 32, and on the other hand a hydraulic piston secondary 34.
  • the interior volume 35 of the hollow movable cylinder 32 communicates with the interior volume V of the master cylinder through openings, such as 36, formed in the movable cylinder in an axial direction.
  • this movable cylinder 32 slides tightly in the body of master cylinder 200, the seal being obtained by at least one annular lip seal 37.
  • the secondary hydraulic piston 34 slides inside the movable cylinder 32, that it seals tightly thanks to an annular seal 38.
  • the movable cylinder 32 is connected, via a ring 40, to the rigid skirt 20 so to receive at least part of the assistance force exerted by this rigid skirt 20.
  • the secondary hydraulic piston 34 is disposed axially, opposite a push rod 42 integral with the plunger 28 and capable of transmitting to it at least the input force exerted on the control rod 26 itself secured to the plunger 28.
  • the different moving parts occupy the position shown in Figures 1 and 2, and in particular the secondary hydraulic piston 34 abuts forwards on a shoulder radial 44 of the movable cylinder 32 under the effect of the bias of a spring 46.
  • the shoulder 44 is formed at the front end of the ring 40.
  • the valve 24 authorizes communication between the two chambers 12 and 14, which are then at the same reduced pressure supplied by fitting 15.
  • a first effort on the brake pedal is used to overcome the spring preload of the brake rod. control 26 and bring the valve 24 in a position where it isolates the two chambers 12 and 14 one from the other. This increased effort on the brake pedal therefore provides no pressure increase in the master cylinder and it is represented on the curve of the Figure 8 by the OA segment.
  • the hydraulic pressure in the internal volume V of the master cylinder 200 then rises and is established, by circulation of hydraulic fluid through the openings 36, in the internal volume 35 of the movable cylinder 32, and is exerted on the section S of the secondary hydraulic piston 34.
  • the actuator jump can be set to any desired value by adjusting the preload at rest of the spring 46.
  • the screwing of the ring 40 in the movable cylinder 32 thus has the effect of compressing the spring 46, therefore increasing the prestress exerted by the latter on the secondary hydraulic piston 34 in the direction of the master cylinder, that is to say to further increase the value of the jump.
  • this ring is for example made in two parts screwed into one another so as to have an adjustable total length.
  • the push rod 42 is itself made in two parts screwed into each other so as to have an adjustable total length, the adjustment of this length making it possible in particular to modify the opening of the valve at the appearance of the jump, whatever the value given to the latter by screwing the ring 40 into the movable cylinder 32.
  • the hydraulic pressure increases in the volumes V and 35, and reaches a predetermined value, for which, applying to section S, it becomes sufficient to overcome the spring preload at rest 46
  • the hydraulic piston secondary 34 then moves backwards and comes into contact with the push rod 42, as illustrated by point B of the curve in Figure 8.
  • a stopper piece 45 of rubber or other elastomeric material at the rear of the hydraulic piston secondary 34, and / or at the front of the push rod 42 to absorb the shock of this contact and noise as a result.
  • the secondary hydraulic piston 34 then exerts on the push rod 42, and on the pedal. brake, a reaction force, depending on the assistance force, opposing the input force, and thus allowing control of the first force by the second, as shown by the segment BC on the curve of Figure 8.
  • the secondary hydraulic piston 34 constitutes then a reaction piston, subjected to the hydraulic pressure prevailing in the reaction chamber constituted by the interior volume 35 of the movable cylinder 32.
  • This segment BC equal to the ratio of the output pressure to the input force, represents the assistance ratio of the braking device.
  • This assistance ratio is also equal to the ratio of the section S 1 of the movable cylinder 32 to the section S of the secondary hydraulic piston 34.
  • the assistance force reaches its maximum when the pressure in the rear chamber of the actuator reaches atmospheric pressure, and therefore cannot increase. We then reach the phenomenon known as saturation, and represented by the CD segment on the curve Figure 8.
  • the present invention achieves this result, that is to say immediately obtaining a high braking pressure in case of emergency braking, by simple, effective means and whose response time is minimal.
  • the second part 52 is in abutment towards the rear, in the rest position, on the first part 50 under the effect of the bias of a second spring 54 disposed between shoulders of the movable cylinder 32 and of this second part 52.
  • the second spring 54 has a prestress at rest lower than that of spring 46.
  • the second part 52 slides tightly in the movable cylinder 32 thanks to the annular seal 38, as described above. It is also provided with a shutter member the axial opening 36 formed in the movable cylinder 32.
  • this closure member consists of a seal annular 56 disposed on the front face of the second part 52 opposite the axial opening 36. It is also possible to provide for the annular seal 56 to be disposed on the movable cylinder 32, at the edge of the axial opening 36.
  • the operating characteristic curve of the braking device then conforms to the curve of Figure 8, passing through points O. A, B, C and D.
  • the additional forward movement of the plunger 28 causes an opening larger valve 24, which allows a pressure rise in the rear chamber 14 faster.
  • the push rod 42 comes into contact with the second part 52 and slides it forward in the first part 50 by compressing the spring 54, and without compress the spring 46 which then only has the effect of maintaining the first part 50 in support on the radial shoulder 44.
  • the annular seal 56 closes the axial passage 36, so that the volume of the reaction chamber is then reduced to volume defined by the annular seal 56.
  • the section S 2 being less than the section S of the second part 52, it therefore follows that in an emergency braking condition, the assistance ratio is greater than that obtained in a normal braking condition.
  • the operation of the braking device is then represented by the segment BE on the curve of Figure 8.
  • this second assistance report can freely choose this second assistance report and give it any desired value, and in particular a high value by choosing for the diameters of the annular seal 56 and of the opening 36 of the low values.
  • the opening 36 must however have a sufficient diameter to allow the hydraulic pressure rise of the reaction chamber 35 under conditions normal operation, without restricting communication with the volume V of the master cylinder.
  • an assisted braking device which has improved operating characteristics in case of emergency braking, since it has then an assistance ratio significantly higher than that which it presents under conditions normal operating conditions.
  • This change of assistance report is obtained automatically without the need for sensors or complex electronic circuitry, by simple operation the fact that, under these extreme conditions, the plunger 28 and the push rod 42 have relative movement with respect to the rigid skirt 20.
  • the means used to obtain this results are relatively simple, and therefore are of reduced cost and reliable operation in all circumstances, both under normal operating conditions and under emergency conditions.
  • the shutter member of the opening 36 carried by the second part 52, has only been modified with respect to the embodiment of FIG. 2.
  • the second part 52 is formed at its front end with an axial extension hollow 58, sliding in an almost leaktight manner in the opening 36.
  • the extension 58 is of more provided at its rear part with openings where communicating the opening 36 with the reaction chamber 35
  • the push rod 42 advances the second part 52.
  • the hollow axial extension 58 then slides in the opening 36 until the openings 60 are obscured.
  • the communication between the volume V of the master cylinder and the reaction chamber 35 is then interrupted, the pressure prevailing inside the master cylinder no longer being exerted while only on the section S 2 of the second part 52 defined by the external diameter of the extension 58.
  • the re-establishment of communication between the front and rear chambers has the effect of rolling back the movable partition 16 and the movable cylinder 32 under the effect of the spring 25, and to lower the pressure in the interior volume V of the master cylinder. Due to this drop in pressure, and the non-perfect seal between the extension 58 and opening 36, the second part 52 can move back enough to discover the openings 60 and communicate the reaction chamber 35 with the interior volume V of the master cylinder. The second part 52 can then move back under the action of the spring 54, and the different moving parts then return to their rest position illustrated in Figure 3.
  • the first part 50 is in abutment forward on the bottom of the movable cylinder 32, and it is pierced with an axial bore 62 in which is susceptible sliding the second part 52 in leaktight fashion using an annular seal 63.
  • the second part 52 is formed at its end front with a hollow axial extension 58, sliding almost watertight in the opening 30, and it is provided at its rear part with openings 60 making communicate the opening 36 with the reaction chamber 35.
  • the push rod 42 advances the second part 52.
  • the hollow axial extension 58 then slides in the opening 36 until the openings 60 are obscured.
  • the communication between the volume V of the master cylinder and the reaction chamber 35 is then interrupted, the pressure prevailing inside the master cylinder no longer being exerted while only on the section S 2 of the second part 52 defined by the external diameter of the extension 58.
  • the first part 50 is a flange bearing on a radial shoulder of the movable cylinder 32 under the action of the spring 46.
  • the second part 52 is capable of sliding in the first part 50 and in the movable cylinder 32 so waterproof thanks to the annular seal 38.
  • the second part 52 is still formed at its front end with the axial extension hollow 58, provided at its rear part with openings 60 making the opening 36 communicate with the reaction chamber 35.
  • the axial extension 58 comprises at its front end a non-return valve 66, allowing the passage of fluid from the reaction chamber 35 to the interior volume V of the master cylinder, but preventing the passage of fluid in the other direction.
  • the axial extension 58 is formed over part of its length with grooves or grooves 68, allowing, in the position shown in Figure 5, communication without restriction between the axial opening 36 and the reaction chamber 35.
  • the operation is similar to that of the preceding embodiments.
  • the pressure prevailing in the interior volume V of the master cylinder is communicated to the reaction chamber 35 through the opening 36, the grooves 68 and the openings 60, to exercise on section S of the second part 52, and make it go back at the same time as the first part 50, thereby providing the desired reaction on the control rod.
  • the push rod 42 advances the second part 52
  • the extension hollow axial 58 then slides in the opening 36 until the grooves 68 are completely located in opening 36.
  • An additional movement forward of the second part 52 is allowed thanks to the non-return valve 66, authorizing the circulation of fluid from the reaction chamber 35 to the interior volume V of the master cylinder.
  • the second part 52 can move back enough to discover the grooves 68 and communicate the reaction chamber 35 with the interior volume V of the master cylinder. The second part 52 can then move back under the action of the spring 54, and the different moving parts then return to their rest position illustrated in Figure 5.
  • the first part 50 is, as in the mode of previous embodiment, a flange bearing on a radial shoulder of the movable cylinder 32 under the action of spring 46, and the second part 52 is capable of sliding in the first part 50 and tightly in the movable cylinder 32 thanks to the annular seal 38.
  • the second part 52 is formed at its front end with an axial extension 70, consisting this time of a full cylinder, and sliding in a quasi-tight way in the axial opening 36, in communication with the interior volume V of the master cylinder.
  • the reaction chamber 35 is then of annular shape.
  • the second part 52 is formed with a peripheral groove 72 in which is arranged a lip seal 74, of the same type as the lip seal 37 used in the master cylinder.
  • the groove 72 is formed between the portion of the second part 52 sliding from tightly in the movable cylinder 32 and a front portion of substantially larger diameter small.
  • the movable cylinder 32 is also formed with an annular groove 76, into which opens a channel 78 formed in the movable cylinder 32 and communicating with the interior volume V of the master cylinder.
  • the annular grooves 72 and 76 are substantially opposite one another, so that the lip seal 74 allows the communication between channel 78 and reaction chamber 35.
  • the push rod 42 advances the second part 52.
  • the extension full axial 70 then slides in the opening 36 until the lip seal 74 leaves the annular groove 76 and ensures a perfect seal between the first and second parts 50 and 52. Additional forward movement of the second part 52 is permitted thanks to lip seal 74, playing the role of a non-return valve, and allowing circulation of fluid from the reaction chamber 35 to the channel 78 and to the interior volume V of the master cylinder.
  • the second part 52 can move back enough to bring the lip seal 74 in groove 76 of movable cylinder 32, and thus allow communication between the reaction chamber 35 and the interior volume V of the master cylinder.
  • the second part 52 can then move back under the action of the spring 54, and the various moving parts resume then their rest position illustrated in Figure 6.
  • the variant embodiment shown in the Figure in fact constitutes an alternative embodiment of the embodiment shown in Figure 4.
  • the first part 50 is in abutment forward on the bottom of the movable cylinder 32, and it is pierced an axial bore 62 in which the second is capable of sliding in leaktight fashion part 52 thanks to an annular seal 63.
  • the second part 52 is of generally cylindrical shape, integral at its front end with a disc 80, with an outside diameter greater than that of bore 62.
  • a third part 82 consists of a piston 82 capable of sliding tightly thanks to an annular seal 83 in a bore 84 of the movable cylinder 32.
  • This third part 82 is biased towards the rear in the rest position by a spring 86 of so as to come into abutment, at rest, on the first part 50, by means of teeth or slots 88.
  • This third part 82 is formed with a through central opening 90, stepped so to provide a shoulder on which a spring 92 bears, also bearing on the disc 80 of the second part 52.
  • the spring preload at rest is less than that of spring 46, and the sum of the prestressed at rest of the springs 86 and 92 is less than that of the spring 46, so that that the second part is, at rest, in front stop on the movable cylinder 32.
  • the spring 92 has a lower stiffness than that of spring 86.
  • the shutter member of the reaction chamber 35 consists of a annular seal 94, has on the second part 52 where, as shown, on the third part 82, around the rear end of the opening 90.
  • the push rod 42 advances the second part 52, which slides then in the bore 62.
  • the stiffness of the spring 86 being greater than that of the spring 92, this last compresses the first and allows the second part to come into contact with the third part, or more exactly of the annular seal 94. In doing so, the communication between the volume V of the master cylinder and the reaction chamber 35 is interrupted.
  • the movement towards the front of the second part / third part set is not limited since this set is moves in the reaction chamber which then has a constant volume.
  • reaction chamber 35 being isolated from the internal volume V of the master cylinder, the pressure prevailing inside the master cylinder no longer exerts itself only on the section S 2 of the second part 52 defined by the internal diameter of the ring seal 94.
  • the spring 86 can push back the third part 82 backwards, until it comes to a stop on the first part 50, while the spring 92 can push back the second part 52 until it also comes into abutment on the first part 50.

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  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Braking Systems And Boosters (AREA)
  • Transmission Of Braking Force In Braking Systems (AREA)
  • Braking Arrangements (AREA)
  • Regulating Braking Force (AREA)

Description

La présente invention concerne les dispositifs de freinage assisté pour vehicules à moteur, comprenant un maítre-cylindre commandant la pression hydraulique dans le circuit de freinage relié aux freins du vehicule, ce maítre-cylindre étant susceptible d'être actionné par un servomoteur pneumatique d'assistance lorsque le conducteur du vehicule appuie sur la pédale de freinage.The present invention relates to assisted braking devices for motor vehicles, comprising a master cylinder controlling the hydraulic pressure in the braking circuit connected to the vehicle brakes, this master cylinder being capable of being actuated by a servomotor assistance tire when the vehicle driver presses the brake pedal braking.

De façon classique. le maítre-cylindre est rempli d'un fluide de fremage et équipé d'un piston hydraulique principal destiné à recevoir une force d'actionnement se composant d'une force d'entrée et d'une force d'assistance agissant toutes deux suivant une direction axiale.Classically. the master cylinder is filled with a freming fluid and fitted with a piston main hydraulics for receiving an actuating force consisting of a force input and assistance force both acting in an axial direction.

D'autre part, le servomoteur pneumatique d'assistance est susceptible d'être commandé par application de la force d'entrée sur une tige de commande contrôlant l'ouverture d'un clapet, pour exercer la force d'actionnement sur le piston hydraulique principal du maítre-cylindre, le servomoteur comportant une enveloppe rigide séparée de façon étanche en deux chambres au moyen d'une cloison mobile susceptible d'être sollicitée par une différence de pression entre les deux chambres résultant de l'ouverture du clapet et d'entraíner un piston pneumatique mobile par rapport à l'enveloppe et portant le clapet, la force d'entrée étant transmise par l'intermédiaire d'un disque de réaction sur lequel s'appuie également le piston pneumatique pour lui fournir une partie au moins de la force d'assistance.On the other hand, the pneumatic booster can be controlled by application of the input force on a control rod controlling the opening of a valve, to exert the actuating force on the main hydraulic piston of the master cylinder, the servomotor comprising a rigid casing separated in a sealed manner into two chambers at by means of a movable partition capable of being stressed by a pressure difference between the two chambers resulting from the opening of the valve and driving a mobile pneumatic piston relative to the casing and carrying the valve, the input force being transmitted through a reaction disc on which the pneumatic piston also rests for him provide at least some of the assist force.

Un dispositif de ce type est bien connu dans l'art antérieur et se trouve par exemple décrit dans le document US-A-4 491 058.A device of this type is well known in the prior art and is for example described in US-A-4,491,058.

Ces dispositifs de freinage présentent comme avantage, résultant de l'utilisation d'un piston pneumatique mobile par rapport à l'enveloppe rigide, que la course totale disponible pour la tige de commande, donc pour la pédale de frein, est relativement longue, ce qui constitue une condition nécessaire pour assurer le contrôle optimal de la décélération du véhicule au freinage.These braking devices have the advantage, resulting from the use of a piston pneumatic movable with respect to the rigid casing, that the total stroke available for the control rod, therefore for the brake pedal, is relatively long, which constitutes a necessary condition to ensure optimal control of the vehicle deceleration when braking.

Cependant, en cas de freinage brusque destiné à pallier à une situation d'urgence, ces dispositifs de freinage présentent l'inconvénient majeur de nécessiter, pour obtenir une pression dans le circuit de freinage relativement élevée, une course de la pédale de freinage sensiblement plus longue que celle qui est nécessaire pour obtenir la même pression dans le circuit lors d'un freinage dans ces conditions habituelles où le caractère d'urgence du freinage se fait moins sentir.However, in the event of sudden braking intended to alleviate an emergency situation, these devices have the major drawback of requiring, in order to obtain pressure in the brake system relatively high, a stroke of the brake pedal significantly more as long as necessary to obtain the same pressure in the circuit during braking under these usual conditions where the urgency of braking is less felt.

Etant donnée l'urgence du freinage, le conducteur ne se rend pas toujours compte de cette course allongée de la pedale de frein, puisqu'il appuie dessus avec une force importante variant rapidement pour obtenir l'effet de freinage imposé par cette situation d'urgence.Given the urgency of braking, the driver is not always aware of this extended stroke of the brake pedal, since it presses on it with a significant varying force quickly to obtain the braking effect imposed by this emergency.

On a alors developpé des systèmes de freinage comportant des capteurs divers sensibles à la force appliquée sur la pédale de freinage et/ou à la vitesse d'application de cette force pour corriger, au moyen d'une électrovalve pneumatique commandée par un microprocesseur recevant les signaux issus de ces capteurs, la différence de pression régnant dans le servomoteur pour la faire augmenter plus rapidement, de façon à augmenter également la force d'assistance plus rapidement et donc de corriger l'allongement du temps de réponse du servomoteur par une augmentation de la force d'assistance.Braking systems were then developed comprising various sensors sensitive to the force applied to the brake pedal and / or at the speed of application of this force to correct, by means of a pneumatic solenoid valve controlled by a receiving microprocessor the signals from these sensors, the pressure difference prevailing in the actuator to make it increase faster, so as to also increase the assistance force faster and therefore correct the lengthening of the servomotor response time by an increase in the assistance force.

Toutefois, bien que les capteurs et le microprocesseur aient des temps de réponse très brefs, les composants mécaniques sur lesquels les capteurs sont installés ont une inertie ou un temps de réponse relativement important, de sorte que le système correcteur électronique n'entre en jeu qu'après un temps relativement long après la détection de la situation d'urgence.However, although the sensors and the microprocessor have very short response times, the mechanical components on which the sensors are installed have an inertia or a time relatively large response, so that the electronic correction system does not come into game only after a relatively long time after the detection of the emergency.

On a développé parallèlement des dispositifs de freinage assisté dans lesquels la réaction s'exerçant sur la tige de commande n'est plus fournie mécaniquement par un disque de réaction, mais par la pression hydraulique régnant dans le maítre-cylindre.In addition, assisted braking devices have been developed in which the reaction acting on the control rod is no longer mechanically supplied by a reaction disk, but by the hydraulic pressure prevailing in the master cylinder.

Dans ces dispositifs, le piston hydraulique principal du maítre cylindre comporte lui-même un cylindre mobile creux, communiquant avec le maítre-cylindre, recevant une partie au moins de la force d'assistance, et à l'intérieur duquel coulisse, de façon étanche et suivant la direction axiale, un piston hydraulique secondaire susceptible de recevoir au moins la force d'entrée, des moyens élastiques exerçant une force élastique entre le piston hydraulique secondaire et le cylindre mobile et sollicitant le piston hydraulique secondaire en direction du maítre-cylindre, au moins une ouverture étant pratiquée dans le cylindre mobile pour faire communiquer l'intérieur de ce dernier avec l'intérieur du maítre-cylindre.In these devices, the main hydraulic piston of the master cylinder itself comprises a hollow mobile cylinder, communicating with the master cylinder, receiving at least part of the assistance force, and inside which slides, tightly and in the direction axial, a secondary hydraulic piston capable of receiving at least the input force, elastic means exerting an elastic force between the secondary hydraulic piston and the cylinder movable and urging the secondary hydraulic piston towards the master cylinder, at at least one opening being made in the movable cylinder to communicate the interior of the latter with the interior of the master cylinder.

Un tel dispositif se trouve par exemple decrit dans le document FR-A-2 658 466.Such a device is for example described in document FR-A-2 658 466.

Ces dispositifs à reaction hydraulique présentent comme avantage principal que, quelles que soient l'intensité de l'action de freinage ou la vitesse d'application de la force d'entrée, leur courbe caractéristique de fonctionnement, à savoir la courbe donnant la pression dans le maítre-cylindre en fonction de l'intensité de la force à l'entrée du servomoteur, est inchangée. Ces dispositifs ne présentent donc pas d'allongement du temps de réponse en cas de freinage d'urgence.The main advantage of these hydraulic reaction devices is that whatever either the intensity of the braking action or the speed of application of the input force, their characteristic operating curve, namely the curve giving the pressure in the master cylinder depending on the intensity of the force at the input of the actuator, is unchanged. These devices therefore do not have an extended response time in the event of braking emergency.

Le fait d'équiper ces dispositifs à réaction hydraulique de capteurs de détection de situation d'urgence et d'une électrovalve pneumatique pour augmenter la pression dans la chambre arrière du servomoteur procure ainsi un net avantage par rapport aux dispositifs à réaction mécanique, puisqu'il contribue à améliorer la courbe de fonctionnement normale du servomoteur, plutôt que de chercher à corriger une courbe de fonctionnement dégradée.Equipping these hydraulic reaction devices with situation detection sensors and a pneumatic solenoid valve to increase the pressure in the rear chamber the servomotor thus provides a clear advantage over mechanical reaction devices, since it contributes to improving the normal operating curve of the servomotor, rather than trying to correct a degraded operating curve.

La présente invention se place dans ce contexte et a pour objet de proposer un dispositif de freinage assisté à réaction hydraulique, qui présente des caractéristiques de fonctionnement améliorées en cas de freinage d'urgence, sans nécessiter de capteurs ni de circuit électronique complexe, et qui soit donc d'un coût réduit, tout en ayant un fonctionnement fiable en toutes circonstances.The present invention is placed in this context and aims to provide a device for assisted hydraulic reaction braking, which has operating characteristics improved in case of emergency braking, without requiring sensors or electronic circuit complex, and which is therefore of reduced cost, while having reliable operation in all circumstances.

Dans ce but, la présente invention propose un dispositif de freinage assisté pour véhicule à moteur, comprenant d'une part un maítre-cylindre rempli d'un fluide de freinage et équipé d'un piston hydraulique principal destiné à recevoir une force d'actionnement se composant d'une force d'entrée et d'une force d'assistance agissant toutes deux suivant une direction axiale, et d'autre part un servomoteur pneumatique d'assistance susceptible d'être commandé par application de la force d'entrée sur une tige de commande solidaire d'un plongeur contrôlant l'ouverture d'un clapet à trois voies, pour exercer la force d'actionnement sur le piston hydraulique principal, le servomoteur comportant une enveloppe rigide séparée de façon étanche en au moins deux chambres au moyen d'au moins une cloison mobile, susceptible d'être sollicitée par une différence de pression entre les deux chambres résultant de l'ouverture du clapet à trois voies et d'entraíner un piston pneumatique, mobile par rapport à l'enveloppe, portant le clapet à trois voies et contribuant au moins à transmettre la force d'assistance, le piston hydraulique principal du maítre cylindre comportant lui-même un cylindre mobile, creux, communiquant avec le volume intérieur du maítre-cylindre, recevant une partie au moins de la force d'assistance, et à l'interieur duquel coulisse, de façon étanche et suivant la direction axiale, un piston hydraulique secondaire susceptible de recevoir au moins la force d'entrée, des premiers moyens élastiques exerçant une première force élastique entre le piston hydraulique secondaire et le cylindre mobile et sollicitant le piston hydraulique secondaire en direction du maítre-cylindre. au moins une ouverture étant pratiquée dans le cylindre mobile pour faire communiquer l'interieur de ce dernier avec l'intérieur au maítre-cylindre, le piston hydraulique secondaire comportant un moyen de clapet à deux voies normalement ouvert, susceptible d'interrompre la communication entre le volume interieur du maítre-cylindre et l'intérieur du cylindre mobile.To this end, the present invention provides an assisted braking device for a vehicle with engine, comprising on the one hand a master cylinder filled with a brake fluid and equipped with a main hydraulic piston intended to receive an actuating force consisting of a input force and assistance force both acting in an axial direction, and on the other hand a pneumatic assistance servomotor capable of being controlled by application of the input force on a control rod secured to a plunger controlling the opening a three-way valve, to exert the actuating force on the hydraulic piston main, the actuator having a rigid envelope separated in a sealed manner at at least two rooms by means of at least one movable partition, capable of being requested by a pressure difference between the two chambers resulting from the opening of the three-way valve tracks and drive a pneumatic piston, movable relative to the casing, carrying the valve to three ways and contributing at least to transmit the assistance force, the hydraulic piston main of the master cylinder itself comprising a mobile, hollow, communicating cylinder with the interior volume of the master cylinder, receiving at least part of the assistance force, and inside which slides, tightly and in the axial direction, a piston secondary hydraulics capable of receiving at least the input force, first means elastics exerting a first elastic force between the secondary hydraulic piston and the movable cylinder and urging the secondary hydraulic piston towards the master cylinder. at least one opening being made in the movable cylinder to communicate the interior of the latter with the interior to the master cylinder, the secondary hydraulic piston comprising a normally open two-way valve means capable of interrupting the communication between the interior volume of the master cylinder and the interior of the movable cylinder.

Un tel dispositif de freinage assiste est par exemple connu du document EP-B-0 662 894.Such an assisted braking device is for example known from document EP-B-0 662 894.

Selon la présente invention, le piston hydraulique secondaire est composite, et comporte une première partie en butée, en position de repos, contre le cylindre mobile sous l'effet des premiers moyens élastiques, et une deuxième partie susceptible de coulisser par rapport à la première partie, des deuxièmes moyens élastiques exerçant vers l'arrière une deuxième force élastique sur la deuxième partie pour la solliciter en butée, en position de repos, contre la première partie.According to the present invention, the secondary hydraulic piston is composite, and comprises a first part in abutment, in the rest position, against the movable cylinder under the effect of the first elastic means, and a second part capable of sliding relative to the first part, second elastic means exerting a second elastic force towards the rear on the second part to urge it into abutment, in the rest position, against the first part.

Grâce à cette disposition, lors d'une action de freinage d'urgence, les première et deuxième parties du piston hydraulique secondaire peuvent coulisser l'une par rapport à l'autre et actionner le moyen de clapet à deux voies dans le sens de la fermeture, de sorte que le piston hydraulique secondaire ne reçoit la réaction de pression interne du maítre-cylindre que sur une section inférieure à celle sur laquelle il reçoit cette reaction de pression lors d'un freinage dans des conditions d'urgence, d'où il resulte que le rapport d'assistance du dispositif de freinage assisté est supérieur en freinage d'urgence à celui qui est obtenu pour un freinage dans des conditions normales.Thanks to this arrangement, during an emergency braking action, the first and second parts of the secondary hydraulic piston can slide relative to each other and actuate the two-way valve means in the closing direction, so that the hydraulic piston secondary receives the internal pressure reaction of the master cylinder only on a section lower than that on which it receives this pressure reaction during braking in emergency conditions, from which it follows that the assistance report of the assisted braking device is greater in emergency braking than that obtained for braking under conditions normal.

D'autres buts, caractéristiques et avantages de l'invention ressortiront clairement de la description qui suit d'un mode de réalisation donné à titre d'exemple nullement limitatif, en référence aux dessins annexés sur lesquels

  • La Figure 1 représente une vue en coupe d'un dispositif de freinage assisté réalisé conformément à la présente invention,
  • La Figure 2 représente une vue en coupe à plus grande échelle de la partie centrale du dispositif de la Figure 1.
  • La Figure 3 représente une vue en coupe d'une première variante de réalisation de la partie centrale du dispositif de freinage de la Figure 1.
  • La Figure 4 représente une vue en coupe d'une deuxième variante de realisation de la partie centrale au dispositif de freinage de la Figure 1,
  • La Figure 5 représente une vue en coupe d'une troisième variante de réalisation de la partie centrale du dispositif de freinage de la Figure 1,
  • La Figure 6 représente une vue en coupe d'une quatrième variante de réalisation de la partie centrale du dispositif de freinage de la Figure 1,
  • La Figure 7 représente une vue en coupe d'une cinquième variante de réalisation de la partie centrale du dispositif de freinage de la Figure 1, et
  • La Figure 8 représente la courbe de la pression engendrée par le maítre-cylindre en fonction de l'effort appliqué à la pédale de freinage, cette courbe étant obtenue avec le dispositif de freinage conforme à la présente invention.
Other objects, characteristics and advantages of the invention will emerge clearly from the following description of an embodiment given by way of nonlimiting example, with reference to the appended drawings in which
  • FIG. 1 represents a sectional view of an assisted braking device produced in accordance with the present invention,
  • Figure 2 shows a sectional view on a larger scale of the central part of the device of Figure 1.
  • FIG. 3 represents a sectional view of a first alternative embodiment of the central part of the braking device of FIG. 1.
  • FIG. 4 represents a sectional view of a second alternative embodiment of the central part of the braking device of FIG. 1,
  • FIG. 5 represents a sectional view of a third alternative embodiment of the central part of the braking device of FIG. 1,
  • FIG. 6 represents a sectional view of a fourth alternative embodiment of the central part of the braking device of FIG. 1,
  • FIG. 7 represents a sectional view of a fifth alternative embodiment of the central part of the braking device of FIG. 1, and
  • Figure 8 shows the pressure curve generated by the master cylinder as a function of the force applied to the brake pedal, this curve being obtained with the braking device according to the present invention.

Dans la mesure où l'invention ne concerne qu'un perfectionnement apporté aux systèmes de freinage à assistance pneumatique, et où la constitution genérale et le fonctionnement de ces derniers sont bien connus de l'homme de l'art, ces systèmes ne seront rapidement rappelés ici que pour permettre une compréhension totale du perfectionnement que représente l'invention.Insofar as the invention relates only to an improvement made to the pneumatic assist braking, and where the general constitution and functioning of these these are well known to those skilled in the art, these systems will not be quickly recalled here only to allow a complete understanding of the improvement represented by the invention.

Schématiquement, un système de ce type comprend un servomoteur 100 et un maítre-cylindre 200.Schematically, a system of this type comprises a servomotor 100 and a master cylinder 200.

Le servomoteur 100 est prévu pour être fixé de façon habituelle sur un tablier (non représenté) de séparation entre un compartiment moteur d'un véhicule et l'habitacle de ce véhicule et pour être actionné par une pédale de freinage (non représentée) située dans cet habitacle. Le maítre-cylindre 200 commandant le circuit de freinage hydraulique du véhicule est fixé sur la paroi avant du servomoteur 100.The servomotor 100 is designed to be fixed in the usual way to an apron (not shown) of separation between an engine compartment of a vehicle and the passenger compartment of this vehicle and for be actuated by a brake pedal (not shown) located in this passenger compartment. The master cylinder 200 controlling the hydraulic brake system of the vehicle is fixed on the wall front of actuator 100.

Par convention, on appelle "avant" de l'ensemble servomoteur/maítre-cylindre la partie de ce dernier tournée vers le maítre-cylindre 200 et "arrière" de cet ensemble la partie tournée vers la pédale de frein 12. Sur les Figures, l'avant est ainsi a gauche et l'arrière à droite. By convention, the part of this servomotor / master cylinder assembly is called "front" last turned towards the master cylinder 200 and "rear" of this assembly, the part facing the brake pedal 12. In the Figures, the front is thus on the left and the rear on the right.

Le servomoteur 100 comprend lui-même une enveloppe rigide dont le volume intérieur est séparé en une chambre avant 12 et une chambre arrière 14, de façon étanche, par une cloison mobile 16 comprenant une membrane 18 et une jupe rigide 20 et susceptible d'entraíner un piston pneumatique 22 mobile a l'interieur de l'enveloppe 10.The servomotor 100 itself comprises a rigid envelope whose internal volume is separated into a front chamber 12 and a rear chamber 14, in leaktight fashion, by a partition mobile 16 comprising a membrane 18 and a rigid skirt 20 and capable of causing a pneumatic piston 22 movable inside the casing 10.

La chambre avant 12, dont la face avant est fermée de façon étanche par le maítre-cylindre 200, est en permanence raccordée à une source de dépression (non representée) à travers un raccord 15. La pression dans la chambre arrière 14 est contrôlee par une valve à trois voies 24, commandée par une tige de commande 26 reliée à la pédale de frein et solidaire d'un plongeur 28.The front chamber 12, the front face of which is closed in a sealed manner by the master cylinder 200, is permanently connected to a vacuum source (not shown) through a connection 15. The pressure in the rear chamber 14 is controlled by a three-way valve 24, controlled by a control rod 26 connected to the brake pedal and secured to a plunger 28.

Lorsque la tige de commande 26 est en position de repos, c'est à dire tirée vers la droite, le clapet 24 établit une communication entre les deux chambres 12 et 14 du servomoteur. La chambre arrière 14 étant alors soumise à la même dépression que la chambre avant 12, le piston 22 est repoussé vers la droite, en position de repos, par un ressort 25.When the control rod 26 is in the rest position, that is to say pulled to the right, the valve 24 establishes communication between the two chambers 12 and 14 of the actuator. The rear chamber 14 then being subjected to the same vacuum as the front chamber 12, the piston 22 is pushed to the right, in the rest position, by a spring 25.

L'actionnement de la tige de commande 26 vers la gauche a pour effet, dans un premier temps, de déplacer le clapet 24 de façon qu'il isole l'une de l'autre les chambres 12 et 14 puis, dans un deuxième temps, de déplacer ce clapet de façon qu'il ouvre la chambre arrière 14 à la pression atmosphérique.The actuation of the control rod 26 to the left has the effect, at first, move valve 24 so that it isolates chambers 12 and 14 from each other, then in a second time, to move this valve so that it opens the rear chamber 14 under pressure atmospheric.

La différence de pression entre les deux chambres 12 et 14 alors ressentie par la membrane 18 exerce sur la cloison mobile 16 une poussée qui tend à la déplacer vers la gauche et à lui permettre d'entraíner le piston 22 qui se déplace à son tour en comprimant le ressort 25.The pressure difference between the two chambers 12 and 14 then felt by the membrane 18 exerts on the movable partition 16 a push which tends to move it to the left and to allow it to drive the piston 22 which in turn moves by compressing the spring 25.

L'effort de freinage exercé sur la tige de commande 26, ou "force d'entrée" et l'effort d'assistance au freinage, ou "force d'assistance", résultant de la poussée de la cloison mobile 16, sont alors, appliqués ensemble suivant l'axe X-X' du servomoteur 100 en direction du maítre-cylindre 200, et se conjuguent pour constituer la force d'actionnement de ce dernier.The braking force exerted on the control rod 26, or "input force" and the assistance force during braking, or "assistance force", resulting from the thrust of the movable partition 16, are then, applied together along the axis XX 'of the servomotor 100 in the direction of the master cylinder 200, and combine to constitute the actuating force of the latter.

De façon plus précise, la force d'actionnement est appliquée sur le piston hydraulique principal 30 du maítre-cylindre et en provoque le déplacement vers la gauche (sur les Figures), ce qui entraíne une élévation de pression du liquide de freinage présent dans le volume intérieur V du maítre-cylindre 200, et un actionnement du frein (non représenté) relié à ce dernierMore precisely, the actuating force is applied to the main hydraulic piston 30 of the master cylinder and causes it to move to the left (in the Figures), which causes an increase in the pressure of the brake fluid present in the interior volume V of the master cylinder 200, and a brake actuation (not shown) connected to the latter

Comme on le voit mieux sur la Figure 2, le piston hydraulique principal 30 est en fait composité et comprend d'une part un cylindre 32 mobile et creux, et d'autre part un piston hydraulique secondaire 34.As best seen in Figure 2, the main hydraulic piston 30 is in fact composite and comprises on the one hand a movable and hollow cylinder 32, and on the other hand a hydraulic piston secondary 34.

Le volume interieur 35 du cylindre mobile creux 32 communique avec le volume intérieur V du maítre-cylindre par l'intermédiaire d'ouvertures, telles que 36, ménagées dans le cylindre mobile suivant une direction axiale.The interior volume 35 of the hollow movable cylinder 32 communicates with the interior volume V of the master cylinder through openings, such as 36, formed in the movable cylinder in an axial direction.

En dehors du passage de fluide que permettent ces ouvertures 36 entre le volume intérieur V du maítre-cylindre 200 et le volume interieur 35 du cylindre mobile 32, ce cylindre mobile 32 coulisse de façon étanche dans le corps du maítre-cylindre 200, l'étanchéité étant obtenue grâce au moins à un joint annulaire à lèvre 37.Outside the fluid passage that these openings 36 allow between the interior volume V of the master cylinder 200 and the interior volume 35 of the movable cylinder 32, this movable cylinder 32 slides tightly in the body of master cylinder 200, the seal being obtained by at least one annular lip seal 37.

Le piston hydraulique secondaire 34, quant à lui, coulisse à l'interieur du cylindre mobile 32, qu'il obture de façon étanche grâce à un joint annulaire 38.The secondary hydraulic piston 34, meanwhile, slides inside the movable cylinder 32, that it seals tightly thanks to an annular seal 38.

Le cylindre mobile 32 est relié, par l'intermediaire d'une bague 40, à la jupe rigide 20 de manière à recevoir une partie au moins de la force d'assistance exercée par cette jupe rigide 20.The movable cylinder 32 is connected, via a ring 40, to the rigid skirt 20 so to receive at least part of the assistance force exerted by this rigid skirt 20.

Le piston hydraulique secondaire 34 est disposé axialement, en regard d'une tige de poussée 42 solidaire du plongeur 28 et susceptible de lui transmettre au moins la force d'entrée exercée sur la tige de commande 26 elle-même solidaire du plongeur 28.The secondary hydraulic piston 34 is disposed axially, opposite a push rod 42 integral with the plunger 28 and capable of transmitting to it at least the input force exerted on the control rod 26 itself secured to the plunger 28.

On va maintenant exposer le fonctionnement du dispositif décrit jusqu'à present.We will now describe the operation of the device described so far.

Au repos, les différentes pièces mobiles occupent la position représentée sur les Figures 1 et 2, et en particulier le piston hydraulique secondaire 34 est en butée vers l'avant sur un épaulement radial 44 du cylindre mobile 32 sous l'effet de la sollicitation d'un ressort 46. Dans l'exemple représenté sur les Figures 1 et 2, l'épaulement 44 est formé à l'extrémité avant de la bague 40. Le clapet 24 autorise la communication entre les deux chambres 12 et 14, qui sont alors à la même pression réduite fournie par le raccord 15.At rest, the different moving parts occupy the position shown in Figures 1 and 2, and in particular the secondary hydraulic piston 34 abuts forwards on a shoulder radial 44 of the movable cylinder 32 under the effect of the bias of a spring 46. In the example shown in FIGS. 1 and 2, the shoulder 44 is formed at the front end of the ring 40. The valve 24 authorizes communication between the two chambers 12 and 14, which are then at the same reduced pressure supplied by fitting 15.

Un premier effort sur la pédale de frein sert à dépasser la précontrainte du ressort de la tige de commande 26 et à amener le clapet 24 dans une position où il isole les deux chambres 12 et 14 l'une de l'autre. Cette augmentation de l'effort sur la pédale de frein ne fournit donc aucune augmentation de pression dans le maitre-cylindre et elle est représentée sur la courbe de la Figure 8 par le segment OA. A first effort on the brake pedal is used to overcome the spring preload of the brake rod. control 26 and bring the valve 24 in a position where it isolates the two chambers 12 and 14 one from the other. This increased effort on the brake pedal therefore provides no pressure increase in the master cylinder and it is represented on the curve of the Figure 8 by the OA segment.

Après cette course prédeterminée de la tige de commande 26, le clapet 24 ouvre a l'atmosphère la chambre arrière 14 du servomoteur 100, et une différence de pressions s'établit entre les deux chambres 12 et 14 du servomoteur. Cette différence de pressions engendre une force d'assistance qui fait avancer la jupe rigide 20 et le cylindre mobile 32.After this predetermined stroke of the control rod 26, the valve 24 opens to the atmosphere the rear chamber 14 of the servomotor 100, and a pressure difference is established between the two chambers 12 and 14 of the servomotor. This difference in pressures generates a force assistance which advances the rigid skirt 20 and the movable cylinder 32.

La pression hydraulique dans le volume interne V du maítre-cylindre 200 s'élève alors et s'établit, par circulation de fluide hydraulique à travers les ouvertures 36, dans le volume interne 35 du cylindre mobile 32, et s'exerce sur la section S du piston hydraulique secondaire 34.The hydraulic pressure in the internal volume V of the master cylinder 200 then rises and is established, by circulation of hydraulic fluid through the openings 36, in the internal volume 35 of the movable cylinder 32, and is exerted on the section S of the secondary hydraulic piston 34.

Dans un premier temps, la force engendrée par cette pression s'exercant sur cette section S ne dépasse pas la précontrainte au repos du ressort 46, de sorte que le piston hydraulique secondaire 34 reste immobile par rapport au cylindre mobile 32, et à distance de la tige de poussée 42, aucune reaction n'étant alors ressentie sur la pédale de frein. Cette première phase de fonctionnement est représentée par le segment AB de la courbe de la Figure 8. La longueur du segment AB est appelée le « saut » du servomoteur.Initially, the force generated by this pressure exerted on this section S does not not exceed the spring preload at rest 46, so that the secondary hydraulic piston 34 remains stationary relative to the movable cylinder 32, and at a distance from the push rod 42, no reaction then being felt on the brake pedal. This first phase of operation is represented by the segment AB of the curve in Figure 8. The length of the segment AB is called the "jump" of the servomotor.

Le saut du servomoteur peut être réglé à toute valeur désirée en ajustant la précontrainte au repos du ressort 46. On peut prévoir par exemple, comme on l'a représenté sur les Figures 1 et 2, que la bague 40 soit filetée et vissée dans le cylindre mobile 32 auquel elle transmet une partie au moins de la force d'assistance s'exerçant sur la jupe 20 en appui contre elle.The actuator jump can be set to any desired value by adjusting the preload at rest of the spring 46. One can provide for example, as shown in Figures 1 and 2, that the ring 40 is threaded and screwed into the movable cylinder 32 to which it transmits part at least the assistance force exerted on the skirt 20 bearing against it.

Le vissage de la bague 40 dans le cylindre mobile 32 a ainsi pour effet de comprimer le ressort 46, donc d'augmenter la précontrainte qu'exerce ce dernier sur le piston hydraulique secondaire 34 en direction du maítre-cylindre, c'est-à-dire encore d'augmenter la valeur du saut.The screwing of the ring 40 in the movable cylinder 32 thus has the effect of compressing the spring 46, therefore increasing the prestress exerted by the latter on the secondary hydraulic piston 34 in the direction of the master cylinder, that is to say to further increase the value of the jump.

Pour compenser la réduction de longueur résultant du vissage de la bague 40 dans le cylindre mobile 32, cette bague est par exemple réalisée en deux parties vissées l'une dans l'autre de manière à présenter une longueur totale réglable.To compensate for the reduction in length resulting from the screwing of the ring 40 in the cylinder mobile 32, this ring is for example made in two parts screwed into one another so as to have an adjustable total length.

On peut également prévoir que la tige de poussée 42 soit elle-même réalisée en deux parties vissées l'une dans l'autre de manière à présenter une longueur totale réglable, le réglage de cette longueur permettant notamment de modifier l'ouverture du clapet à l'apparition du saut, quelle que soit la valeur donnée à ce dernier par vissage de la bague 40 dans le cylindre mobile 32. One can also provide that the push rod 42 is itself made in two parts screwed into each other so as to have an adjustable total length, the adjustment of this length making it possible in particular to modify the opening of the valve at the appearance of the jump, whatever the value given to the latter by screwing the ring 40 into the movable cylinder 32.

Dans une deuxième phase de fonctionnement, la pression hydraulique augmente dans les volumes V et 35, et atteint une valeur prédéterminée, pour laquelle, s'appliquant sur la section S, elle devient suffisante pour vaincre la précontrainte au repos du ressort 46 Le piston hydraulique secondaire 34 se déplace alors vers l'arrière et vient au contact de la tige de poussée 42, comme illustré par le point B de la courbe de la Figure 8. On pourra avantageusement prévoir une pièce de butée 45 en caoutchouc ou un autre matériau elastomère à l'arrière du piston hydraulique secondaire 34, et/ou à l'avant de la tige de poussée 42 pour amortir le choc de ce contact et le bruit en resultant.In a second operating phase, the hydraulic pressure increases in the volumes V and 35, and reaches a predetermined value, for which, applying to section S, it becomes sufficient to overcome the spring preload at rest 46 The hydraulic piston secondary 34 then moves backwards and comes into contact with the push rod 42, as illustrated by point B of the curve in Figure 8. We can advantageously provide a stopper piece 45 of rubber or other elastomeric material at the rear of the hydraulic piston secondary 34, and / or at the front of the push rod 42 to absorb the shock of this contact and noise as a result.

Le piston hydraulique secondaire 34 exerce alors sur la tige de poussée 42, et sur la pédale de frein, une force de réaction, dépendant de la force d'assistance, s'opposant à la force d'entrée, et permettant donc le contrôle de la première force par la seconde, comme on l'a représenté par le segment BC sur la courbe de la Figure 8. Le piston hydraulique secondaire 34 constitue alors un piston de réaction, soumis à la pression hydraulique régnant dans la chambre de réaction constituée par le volume interieur 35 du cylindre mobile 32.The secondary hydraulic piston 34 then exerts on the push rod 42, and on the pedal. brake, a reaction force, depending on the assistance force, opposing the input force, and thus allowing control of the first force by the second, as shown by the segment BC on the curve of Figure 8. The secondary hydraulic piston 34 constitutes then a reaction piston, subjected to the hydraulic pressure prevailing in the reaction chamber constituted by the interior volume 35 of the movable cylinder 32.

La pente de ce segment BC, égale au rapport de la pression de sortie sur la force d'entrée, représente le rapport d'assistance du dispositif de freinage. Ce rapport d'assistance est aussi égal au rapport de la section S1 du cylindre mobile 32 sur la section S du piston hydraulique secondaire 34.The slope of this segment BC, equal to the ratio of the output pressure to the input force, represents the assistance ratio of the braking device. This assistance ratio is also equal to the ratio of the section S 1 of the movable cylinder 32 to the section S of the secondary hydraulic piston 34.

La force d'assistance atteint son maximum lorsque la pression dans la chambre arrière du servomoteur atteint la pression atmosphérique, et ne peut donc plus augmenter. On atteint alors le phénomène connu sous le nom de saturation, et représenté par le segment CD sur la courbe de la Figure 8.The assistance force reaches its maximum when the pressure in the rear chamber of the actuator reaches atmospheric pressure, and therefore cannot increase. We then reach the phenomenon known as saturation, and represented by the CD segment on the curve Figure 8.

Dans toutes ces phases de fonctionnement, on voit notamment que, mise à part la course du plongeur 28 nécessaire pour actionner le clapet 24 et faire varier la pression dans la chambre arrière 14, et correspondant au segment OA de la courbe de la Figure 8, le plongeur 28 et la tige de poussée 42 se déplacent avec la cloison mobile 16.In all these operating phases, we see in particular that, apart from the stroke of the plunger 28 necessary to actuate the valve 24 and vary the pressure in the chamber rear 14, and corresponding to the segment OA of the curve of FIG. 8, the plunger 28 and the push rod 42 move with the movable partition 16.

Le fonctionnement du dispositif de freinage que l'on vient de décrire se reproduit à chaque action de freinage, quelle que soit la vitesse d'application de la force d'entrée sur la tige de commande 26, c'est à dire aussi bien pour un freinage normal où une faible décélération du véhicule est désirée, que pour un freinage d'urgence où le conducteur éprouve le besoin d'arrêter immédiatement son véhicule. The operation of the braking device which has just been described reproduces each time braking action, regardless of the speed at which the input force is applied to the rod command 26, i.e. both for normal braking where a slight deceleration of the vehicle is desired, only for emergency braking where the driver feels the need stop your vehicle immediately.

Dans ce dernier cas, il est bien sûr desirable d'obtenir rapidement un effort de freinage important, c'est à dire une pression élevée dans le circuit hydraulique de freinage. La solution connue, rappelée en préambule, et consistant par exemple à disposer au moins un capteur de force sur la pédale de freinage, et à calculer la vitesse de variation de cette force pour en déduire une situation d'urgence et activer une électrovalve pour mettre la chambre arrière au servomoteur directement à l'atmosphère, n'est qu'un palliatif puisqu'elle ne produit ses effets qu'après un certain temps de retard.In the latter case, it is of course desirable to obtain a significant braking force quickly, i.e. a high pressure in the hydraulic braking circuit. The known solution, recalled in the preamble, and consisting for example of having at least one force sensor on the brake pedal, and to calculate the speed of variation of this force to deduce a emergency situation and activate a solenoid valve to put the rear chamber to the servomotor directly to the atmosphere, is only a palliative since it produces its effects only after a some time late.

La présente invention permet d'atteindre ce résultat, c'est à dire obtenir immédiatement une pression de freinage élevée en cas de freinage d'urgence, par des moyens simples, efficaces et dont le temps de réponse est minimal.The present invention achieves this result, that is to say immediately obtaining a high braking pressure in case of emergency braking, by simple, effective means and whose response time is minimal.

Comme on le voit mieux sur la Figure 2, le piston de réaction 34 est lui-même composité. Il comporte une première partie 50, en butée, en position de repos, sur le cylindre mobile 32 sous l'effet de la sollicitation du ressort 46. Il comporte également une deuxième partie 52, susceptible de coulisser à l'intérieur de la première partie 50.As best seen in Figure 2, the reaction piston 34 is itself composite. he comprises a first part 50, in abutment, in the rest position, on the movable cylinder 32 under the effect of the biasing of the spring 46. It also has a second part 52, capable of to slide inside the first part 50.

La deuxième partie 52 est en butée vers l'arrière, en position de repos, sur la première partie 50 sous l'effet de la sollicitation d'un deuxième ressort 54 disposé entre des épaulements du cylindre mobile 32 et de cette deuxième partie 52. Le deuxième ressort 54 a une précontrainte au repos inférieur a celle du ressort 46.The second part 52 is in abutment towards the rear, in the rest position, on the first part 50 under the effect of the bias of a second spring 54 disposed between shoulders of the movable cylinder 32 and of this second part 52. The second spring 54 has a prestress at rest lower than that of spring 46.

La deuxième partie 52 coulisse de façon étanche dans le cylindre mobile 32 grâce au joint annulaire 38, comme on l'a décrit plus haut. Elle est de plus munie d'un organe d'obturation de l'ouverture axiale 36 ménagée dans le cylindre mobile 32.The second part 52 slides tightly in the movable cylinder 32 thanks to the annular seal 38, as described above. It is also provided with a shutter member the axial opening 36 formed in the movable cylinder 32.

Selon le mode de réalisation de la Figure 2, cet organe d'obturation est constitué d'un joint annulaire 56 disposé sur la face avant de la deuxième partie 52 en regard de l'ouverture axiale 36. On peut également prévoir que le joint annulaire 56 soit disposé sur le cylindre mobile 32, au bord de l'ouverture axiale 36.According to the embodiment of Figure 2, this closure member consists of a seal annular 56 disposed on the front face of the second part 52 opposite the axial opening 36. It is also possible to provide for the annular seal 56 to be disposed on the movable cylinder 32, at the edge of the axial opening 36.

Lorsqu'un effort est appliqué sur la pédale de frein pour une action de freinage où seul un ralentissement normal du vehicule est desiré, l'ensemble que l'on vient de décrire fonctionne comme on l'a expliqué plus haut. En effet, les première et deuxième phases de fonctionnement se déroulent comme on l'a décrit, les première et deuxième parties se déplaçant ensemble vers l'arrière lorsque la pression hydraulique augmente dans la chambre de réaction 35. When a force is applied to the brake pedal for a braking action where only a deceleration normal vehicle is desired, the assembly just described works as explained above. Indeed, the first and second operating phases unfold as described, the first and second parts moving together towards the rear when the hydraulic pressure increases in the reaction chamber 35.

La courbe caractéristique de fonctionnement du dispositif de freinage est alors conforme à la courbe de la Figure 8, en passant par les points O. A, B, C et D.The operating characteristic curve of the braking device then conforms to the curve of Figure 8, passing through points O. A, B, C and D.

Par contre, lors d'une action de freinage dans des conditions d'urgence, c'est à dire quand l'effort d'entrée sur la pédale de frein augmente très rapidement pour atteindre une valeur très élevée, le plongeur 28 et la tige de poussée 42 avancent très rapidement, et en particulier ils avancent par rapport à la jupe rigide 20, la différence de pressions entre les chambres avant et arrière n'ayant pas eu le temps de s'établir et de mouvoir la cloison mobile 16. Ce phénomène a deux conséquences importantes.On the other hand, during a braking action in emergency conditions, that is to say when the input force on the brake pedal increases very quickly to reach a very low value high, the plunger 28 and the push rod 42 advance very rapidly, and in particular they advance with respect to the rigid skirt 20, the pressure difference between the front chambers and rear having not had time to settle down and move the movable partition 16. This phenomenon has two important consequences.

D'une part, le mouvement supplémentaire vers l'avant du plongeur 28 provoque une ouverture plus importante du clapet 24, ce qui permet une montée en pression dans la chambre arrière 14 plus rapide.On the one hand, the additional forward movement of the plunger 28 causes an opening larger valve 24, which allows a pressure rise in the rear chamber 14 faster.

D'autre part, et simultanément, la tige de poussée 42 vient au contact de la deuxième partie 52 et la fait coulisser vers l'avant dans la première partie 50 en comprimant le ressort 54, et sans comprimer le ressort 46 qui n'a alors pour seul effet que de maintenir la première partie 50 en appui sur l'epaulement radial 44. Dans ce mouvement, le joint annulaire 56 vient obturer le passage axial 36, de sorte que le volume de la chambre de réaction se trouve alors réduit au volume défini par le joint annulaire 56.On the other hand, and simultaneously, the push rod 42 comes into contact with the second part 52 and slides it forward in the first part 50 by compressing the spring 54, and without compress the spring 46 which then only has the effect of maintaining the first part 50 in support on the radial shoulder 44. In this movement, the annular seal 56 closes the axial passage 36, so that the volume of the reaction chamber is then reduced to volume defined by the annular seal 56.

Il s'ensuit que la pression hydraulique dans le volume V du maítre-cylindre s'exerce sur la deuxième partie 52, sur sa section S2 définie par le diamètre intérieur du joint annulaire 56. Il en résulte donc que le rapport d'assistance dans cette condition de freinage d'urgence est égal au rapport de la section S1 du cylindre mobile 32 sur la section S2 de la deuxième partie 52 du piston hydraulique secondaire 34 sur laquelle la pression hydraulique s'exerce.It follows that the hydraulic pressure in the volume V of the master cylinder is exerted on the second part 52, on its section S 2 defined by the internal diameter of the annular seal 56. It therefore follows that the assistance ratio in this emergency braking condition is equal to the ratio of the section S 1 of the movable cylinder 32 to the section S 2 of the second part 52 of the secondary hydraulic piston 34 on which the hydraulic pressure is exerted.

La section S2 étant inférieure à la section S de la deuxième partie 52, il en résulte alors que dans une condition de freinage d'urgence, le rapport d'assistance est supérieur à celui qu'on obtient dans une condition de freinage normal. Le fonctionnement du dispositif de freinage est alors représenté par le segment BE sur la courbe de la Figure 8.The section S 2 being less than the section S of the second part 52, it therefore follows that in an emergency braking condition, the assistance ratio is greater than that obtained in a normal braking condition. The operation of the braking device is then represented by the segment BE on the curve of Figure 8.

On voit ainsi que pour un même effort d'entrée instantané P1, on obtient une pression instantanée P2 notablement supérieure à la pression instantanée P1 obtenue dans des conditions de freinage normal. D'autre part, le rapport d'assistance étant supérieur, on atteint plus vite le phénomène de saturation, représenté par le point E. It can thus be seen that for the same instantaneous input force P 1 , an instantaneous pressure P 2 is obtained which is significantly greater than the instantaneous pressure P 1 obtained under normal braking conditions. On the other hand, the assistance ratio being higher, the saturation phenomenon, represented by the point E, is reached more quickly.

On pourra librement choisir ce deuxième rapport d'assistance et lui donner toute valeur desirée, et en particulier une valeur élevée en choisissant pour les diamètres du joint annulaire 56 et de l'ouverture 36 des valeurs faibles. L'ouverture 36 doit toutefois avoir un diamètre suffisant pour permettre la montée en pression hydraulique de la chambre de réaction 35 dans des conditions normales de fonctionnement, sans apporter de restriction dans la communication avec le volume V du maítre-cylindre.We can freely choose this second assistance report and give it any desired value, and in particular a high value by choosing for the diameters of the annular seal 56 and of the opening 36 of the low values. The opening 36 must however have a sufficient diameter to allow the hydraulic pressure rise of the reaction chamber 35 under conditions normal operation, without restricting communication with the volume V of the master cylinder.

Lorsque le conducteur relâche son effort après une telle action de freinage d'urgence, le retour vers l'arrière de la tige de commande 26 a pour effet de mouvoir le plongeur 28 et le clapet 24 qui remet alors les chambres avant et arrière en communication l'une avec l'autre. Il en résulte alors un recul de la cloison mobile 16 et du cylindre mobile 32 sous l'effet du ressort 25, une baisse de pression dans le volume intérieur V du maítre-cylindre, et un recul de la deuxième partie 52 sous l'effet du ressort 54. Les différentes pièces mobiles reprennent alors leur position de repos illustrée sur les Figures 1 et 2.When the driver releases his effort after such an emergency braking action, the return towards the rear of the control rod 26 has the effect of moving the plunger 28 and the valve 24 which then puts the front and rear chambers back into communication with each other. The result then a retraction of the movable partition 16 and of the movable cylinder 32 under the effect of the spring 25, a pressure drop in the interior volume V of the master cylinder, and a drop in the second part 52 under the effect of the spring 54. The different moving parts then resume their position rest shown in Figures 1 and 2.

On a donc bien réalisé, selon la présente invention, un dispositif de freinage assisté qui présente des caractéristiques de fonctionnement améliorées en cas de freinage d'urgence, puisqu'il présente alors un rapport d'assistance nettement supérieur à celui qu'il présente dans des conditions normales de fonctionnement. Ce changement de rapport d'assistance est obtenu automatiquement sans nécessiter de capteurs ni de circuit électronique complexe, par la simple exploitation du fait que, dans ces conditions extrêmes, le plongeur 28 et la tige de poussée 42 présentent un mouvement relatif par rapport à la jupe rigide 20. Les moyens utilisés pour obtenir ce résultat sont relativement simples, et sont donc de coût réduit et de fonctionnement fiable en toutes circonstances, aussi bien dans des conditions normales de fonctionnement que dans des conditions d'urgence.We have therefore produced, according to the present invention, an assisted braking device which has improved operating characteristics in case of emergency braking, since it has then an assistance ratio significantly higher than that which it presents under conditions normal operating conditions. This change of assistance report is obtained automatically without the need for sensors or complex electronic circuitry, by simple operation the fact that, under these extreme conditions, the plunger 28 and the push rod 42 have relative movement with respect to the rigid skirt 20. The means used to obtain this results are relatively simple, and therefore are of reduced cost and reliable operation in all circumstances, both under normal operating conditions and under emergency conditions.

On a représenté sur les Figures 3 à 7 diverses variantes de réalisation du dispositif de freinage assisté qui vient d'être décrit. Sur ces Figures les mêmes éléments sont affectés des mêmes signes de référence.There are shown in Figures 3 to 7 various embodiments of the braking device assisted which has just been described. In these Figures the same elements are assigned the same reference signs.

On voit sur la Figure 3 que l'organe d'obturation de l'ouverture 36, porté par la deuxième partie 52, a seul été modifie par rapport au mode de realisation de la Figure 2. Selon cette variante, la deuxieme partie 52 est formée à son extrémité avant avec un prolongement axial creux 58, coulissant de façon quasi-étanche dans l'ouverture 36. Le prolongement 58 est de plus muni à sa partie arrière d'ouvertures où faisant communiquer l'ouverture 36 avec la chambre de reaction 35We see in Figure 3 that the shutter member of the opening 36, carried by the second part 52, has only been modified with respect to the embodiment of FIG. 2. According to this variant, the second part 52 is formed at its front end with an axial extension hollow 58, sliding in an almost leaktight manner in the opening 36. The extension 58 is of more provided at its rear part with openings where communicating the opening 36 with the reaction chamber 35

Le fonctionnement est identique à celui qui a été décrit plus haut. Lors d'un freinage dans des conditions normales, la pression régnant dans le volume intérieur V du maítre-cylindre est communiquée à la chambre de reaction 35 par les ouvertures 36 et 60, pour s'exercer sur la section S de la deuxième partie 52, et la faire reculer en même temps que la première partie 50.The operation is identical to that which has been described above. When braking in normal conditions, the pressure prevailing in the interior volume V of the master cylinder is communicated to the reaction chamber 35 through the openings 36 and 60, to act on the section S of the second part 52, and make it go back at the same time as the first part 50.

Lors d'un freinage d'urgence, la tige de poussée 42 fait avancer la seconde partie 52. Le prolongement axial creux 58 coulisse alors dans l'ouverture 36 jusqu'à ce que les ouvertures 60 soient occultées. La communication entre le volume V du maítre-cylindre et la chambre de réaction 35 est alors interrompue, la pression régnant à l'intérieur du maítre-cylindre ne s'exerçant plus alors que sur la section S2 de la deuxième partie 52 définie par le diamètre externe du prolongement 58.During emergency braking, the push rod 42 advances the second part 52. The hollow axial extension 58 then slides in the opening 36 until the openings 60 are obscured. The communication between the volume V of the master cylinder and the reaction chamber 35 is then interrupted, the pressure prevailing inside the master cylinder no longer being exerted while only on the section S 2 of the second part 52 defined by the external diameter of the extension 58.

Lorsque le conducteur relâche son effort, le rétablissement de la communication entre les chambres avant et arrière a pour effet de faire reculer la cloison mobile 16 et le cylindre mobile 32 sous l'effet du ressort 25, et de faire baisser la pression dans le volume intérieur V du maítre-cylindre. Du fait de cette baisse de pression, et de l'étanchéité non parfaite entre le prolongement 58 et l'ouverture 36, la deuxième partie 52 peut reculer suffisamment pour découvrir les ouvertures 60 et faire communiquer la chambre de réaction 35 avec le volume intérieur V du maítre-cylindre. La deuxième partie 52 peut alors reculer sous l'action du ressort 54, et les différentes pièces mobiles reprennent alors leur position de repos illustrée sur la Figure 3.When the driver releases his effort, the re-establishment of communication between the front and rear chambers has the effect of rolling back the movable partition 16 and the movable cylinder 32 under the effect of the spring 25, and to lower the pressure in the interior volume V of the master cylinder. Due to this drop in pressure, and the non-perfect seal between the extension 58 and opening 36, the second part 52 can move back enough to discover the openings 60 and communicate the reaction chamber 35 with the interior volume V of the master cylinder. The second part 52 can then move back under the action of the spring 54, and the different moving parts then return to their rest position illustrated in Figure 3.

L'avantage de cette variante réside dans le fait que la section S2 peut être définie avec plus de précision que dans le mode de réalisation précédent.The advantage of this variant resides in the fact that the section S 2 can be defined with more precision than in the previous embodiment.

Selon la variante représentée sur la Figure 4, la première partie 50 est en butée vers l'avant sur le fond du cylindre mobile 32, et elle est percée d'un alésage axial 62 dans lequel est susceptible de coulisser de façon étanche la deuxième partie 52 grâce à un joint annulaire 63.According to the variant shown in Figure 4, the first part 50 is in abutment forward on the bottom of the movable cylinder 32, and it is pierced with an axial bore 62 in which is susceptible sliding the second part 52 in leaktight fashion using an annular seal 63.

La deuxième partie 52 est de forme générale cylindrique, et comporte dans sa partie médiane une collerette 64 venant en butée vers l'arrière sue la première partie 50 sous l'effet de la sollicitation du ressort 54.The second part 52 is of generally cylindrical shape, and comprises in its middle part a flange 64 abutting backwards on the first part 50 under the effect of the stress spring 54.

Comme dans le mode de réalisation de la Figure 3, la deuxième partie 52 est formée à son extrémité avant avec un prolongement axial creux 58, coulissant de façon quasi-étanche dans l'ouverture 30, et il est muni à sa partie arrière d'ouvertures 60 faisant communiquer l'ouverture 36 avec la chambre de reaction 35.As in the embodiment of Figure 3, the second part 52 is formed at its end front with a hollow axial extension 58, sliding almost watertight in the opening 30, and it is provided at its rear part with openings 60 making communicate the opening 36 with the reaction chamber 35.

Le fonctionnement est identique à celui ces modes de réalisation precédents. Lors d'un freinage dans des conditions normales, la pression régnant dans le volume intérieur V du maítre-cylindre est communiquée à la chambre de reaction 35 par les ouvertures 36 et 60, pour s'exercer sur la section S de la premiere partie 50, et la faire reculer en même temps que la deuxième partie 52 grâce á l'étanchéite du joint annulaire 63.The operation is identical to that of these previous embodiments. When braking under normal conditions, the pressure prevailing in the interior volume V of the master cylinder is communicated to the reaction chamber 35 through the openings 36 and 60, for practice on section S of the first part 50, and make it move back at the same time as the second part 52 thanks to the sealing of the annular seal 63.

Lors d'un freinage d'urgence, la tige de poussée 42 fait avancer la seconde partie 52. Le prolongement axial creux 58 coulisse alors dans l'ouverture 36 jusqu'à ce que les ouvertures 60 soient occultées. La communication entre le volume V du maítre-cylindre et la chambre de réaction 35 est alors interrompue, la pression régnant a l'intérieur du maítre-cylindre ne s'exerçant plus alors que sur la section S2 de la deuxième partie 52 définie par le diamètre externe du prolongement 58.During emergency braking, the push rod 42 advances the second part 52. The hollow axial extension 58 then slides in the opening 36 until the openings 60 are obscured. The communication between the volume V of the master cylinder and the reaction chamber 35 is then interrupted, the pressure prevailing inside the master cylinder no longer being exerted while only on the section S 2 of the second part 52 defined by the external diameter of the extension 58.

Lorsque le conducteur relâche son effort, comme dans le mode de réalisation précédent, le recul de la cloison mobile 16 et du cylindre mobile 32 sous l'effet du ressort 25 a pour effet de faire baisser la pression dans le volume interieur V du maítre-cylindre. Du fait de cette baisse de pression, et de l'étanchéité non parfaite entre le prolongement 58 et l'ouverture 36, la deuxième partie 52 peut reculer suffisamment pour découvrir les ouvertures 60 et faire communiquer la chambre de réaction 35 avec le volume intérieur V du maítre-cylindre. La deuxième partie 52 peut alors reculer sous l'action du ressort 54, et les différentes pièces mobiles reprennent alors leur position de repos illustrée sur la Figure 4.When the driver releases his effort, as in the previous embodiment, the retraction of the movable partition 16 and of the movable cylinder 32 under the effect of the spring 25 has the effect of lower the pressure in the interior volume V of the master cylinder. Because of this drop pressure, and not perfect sealing between the extension 58 and the opening 36, the second part 52 can move back enough to discover the openings 60 and communicate the reaction chamber 35 with the internal volume V of the master cylinder. The second part 52 can then move back under the action of spring 54, and the various moving parts then resume their rest position illustrated in Figure 4.

Selon la variante représentée sur la Figure 5, la première partie 50 est une collerette en appui sur un épaulement radial du cylindre mobile 32 sous l'action du ressort 46. La deuxième partie 52 est susceptible de coulisser dans la première partie 50 et dans le cylindre mobile 32 de façon étanche grâce au joint annulaire 38.According to the variant shown in Figure 5, the first part 50 is a flange bearing on a radial shoulder of the movable cylinder 32 under the action of the spring 46. The second part 52 is capable of sliding in the first part 50 and in the movable cylinder 32 so waterproof thanks to the annular seal 38.

La deuxième partie 52 est encore formée à son extrémite avant avec le prolongement axial creux 58, muni à sa partie arrière d'ouvertures 60 faisant communiquer l'ouverture 36 avec la chambre de réaction 35.The second part 52 is still formed at its front end with the axial extension hollow 58, provided at its rear part with openings 60 making the opening 36 communicate with the reaction chamber 35.

Selon cette variante, le prolongement axial 58 comporte à son extrémité avant un clapet anti-retour 66, autorisant le passage de fluide de la chambre de reaction 35 vers le volume interieur V du maítre-cylindre, mais interdisant le passage de fluide dans l'autre sens.According to this variant, the axial extension 58 comprises at its front end a non-return valve 66, allowing the passage of fluid from the reaction chamber 35 to the interior volume V of the master cylinder, but preventing the passage of fluid in the other direction.

De plus, le prolongement axial 58 est formé sur une partie de sa longueur avec des gorges ou des rainures 68, permettant, dans la position représentée sur la Figure 5, une communication sans restriction entre l'ouverture axiale 36 et la chambre de reaction 35. La partie du prolongement axial 58 dépourvue de rainures 68 située en arrière de ces rainures 68, coulisse dans l'ouverture 36 de façon quasi-étanche.In addition, the axial extension 58 is formed over part of its length with grooves or grooves 68, allowing, in the position shown in Figure 5, communication without restriction between the axial opening 36 and the reaction chamber 35. The part of the extension axial 58 without grooves 68 located behind these grooves 68, slides in the opening 36 in a quasi-sealed manner.

Le fonctionnement est voisin de celui des modes de réalisation precédents. Lors d'un freinage dans des conditions normales, la pression régnant dans le volume intérieur V du maítre-cylindre est communiquée à la chambre de réaction 35 par l'ouverture 36, les rainures 68 et les ouvertures 60, pour s'exercer sur la section S de la deuxième partie 52, et la faire reculer en même temps que la première partie 50, procurant ainsi la réaction voulue sur la tige de commande.The operation is similar to that of the preceding embodiments. When braking under normal conditions, the pressure prevailing in the interior volume V of the master cylinder is communicated to the reaction chamber 35 through the opening 36, the grooves 68 and the openings 60, to exercise on section S of the second part 52, and make it go back at the same time as the first part 50, thereby providing the desired reaction on the control rod.

Lors d'un freinage d'urgence, la tige de poussée 42 fait avancer la seconde partie 52 Le prolongement axial creux 58 coulisse alors dans l'ouverture 36 jusqu'à ce que les rainures 68 soient complètement situées dans l'ouverture 36. Un mouvement supplémentaire vers l'avant de la deuxième partie 52 est permis grâce au clapet anti-retour 66, autorisant la circulation de fluide de la chambre de réaction 35 vers le volume intérieur V du maítre-cylindre.During emergency braking, the push rod 42 advances the second part 52 The extension hollow axial 58 then slides in the opening 36 until the grooves 68 are completely located in opening 36. An additional movement forward of the second part 52 is allowed thanks to the non-return valve 66, authorizing the circulation of fluid from the reaction chamber 35 to the interior volume V of the master cylinder.

La communication de fluide du volume V du maítre-cylindre vers la chambre de réaction 35 étant alors interrompue, la pression régnant à l'intérieur du maítre-cylindre ne s'exerce plus alors que sur la section S2 de la deuxième partie 52 définie par le diamètre externe du prolongement 58, comme dans les modes de réalisation précédents.The fluid communication of the volume V of the master cylinder towards the reaction chamber 35 being then interrupted, the pressure prevailing inside the master cylinder no longer exerts itself only on the section S 2 of the defined second part 52 by the external diameter of the extension 58, as in the previous embodiments.

Lorsque le conducteur relâche son effort, la pression baisse dans le volume intérieur V du maítre-cylindre. Du fait de cette baisse de pression, et de l'étanchéité non parfaite entre le prolongement 58 et l'ouverture 36, la deuxième partie 52 peut reculer suffisamment pour découvrir les rainures 68 et faire communiquer la chambre de réaction 35 avec le volume intérieur V du maítre-cylindre. La deuxième partie 52 peut alors reculer sous l'action du ressort 54, et les différentes pièces mobiles reprennent alors leur position de repos illustrée sur la Figure 5.When the driver releases his effort, the pressure drops in the interior volume V of the master cylinder. Due to this drop in pressure, and the non-perfect seal between the extension 58 and opening 36, the second part 52 can move back enough to discover the grooves 68 and communicate the reaction chamber 35 with the interior volume V of the master cylinder. The second part 52 can then move back under the action of the spring 54, and the different moving parts then return to their rest position illustrated in Figure 5.

Selon la variante représentée sur la Figure 6, la première partie 50 est, comme dans le mode de réalisation précédent, une collerette en appui sur un épaulement radial du cylindre mobile 32 sous l'action du ressort 46, et la deuxième partie 52 est susceptible de coulisser dans la première partie 50 et de façon étanche dans le cylindre mobile 32 grâce au joint annulaire 38. According to the variant shown in Figure 6, the first part 50 is, as in the mode of previous embodiment, a flange bearing on a radial shoulder of the movable cylinder 32 under the action of spring 46, and the second part 52 is capable of sliding in the first part 50 and tightly in the movable cylinder 32 thanks to the annular seal 38.

La deuxième partie 52 est formée à son extrémité avant avec un prolongement axial 70, constitué cette fois d'un cylindre plein, et coulissant de façon quasi-étanche dans l'ouverture axiale 36, en communication avec le volume intérieur V du maítre-cylindre. La chambre de réaction 35 est alors de forme annulaire.The second part 52 is formed at its front end with an axial extension 70, consisting this time of a full cylinder, and sliding in a quasi-tight way in the axial opening 36, in communication with the interior volume V of the master cylinder. The reaction chamber 35 is then of annular shape.

Selon cette variante, la deuxième partie 52 est formée avec une gorge périphérique 72 dans laquelle est disposé un joint à lèvre 74, de même type que le joint à lèvre 37 utilisé dans le maítre-cylindre. La gorge 72 est formée entre la portion de la deuxième partie 52 coulissant de façon étanche dans le cylindre mobile 32 et une portion avant de diamètre sensiblement plus petit.According to this variant, the second part 52 is formed with a peripheral groove 72 in which is arranged a lip seal 74, of the same type as the lip seal 37 used in the master cylinder. The groove 72 is formed between the portion of the second part 52 sliding from tightly in the movable cylinder 32 and a front portion of substantially larger diameter small.

Le cylindre mobile 32 est également formé avec une gorge annulaire 76, dans laquelle débouche un canal 78 formé dans le cylindre mobile 32 et communiquant avec le volume intérieur V du maítre-cylindre. Dans la position de repos représentée sur la Figure 6, les gorges annulaires 72 et 76 sont sensiblement l'une en face de l'autre, de sorte que le joint à lèvre 74 autorise la communication entre le canal 78 et la chambre de réaction 35.The movable cylinder 32 is also formed with an annular groove 76, into which opens a channel 78 formed in the movable cylinder 32 and communicating with the interior volume V of the master cylinder. In the rest position shown in Figure 6, the annular grooves 72 and 76 are substantially opposite one another, so that the lip seal 74 allows the communication between channel 78 and reaction chamber 35.

Lors d'un freinage dans des conditions normales, la pression régnant dans le volume intérieur V du maítre-cylindre s'exerce d'une part dans la chambre de réaction annulaire 35 par le canal 78 et les gorges 76 et 72, et d'autre part sur le prolongement axial 70 de la deuxième partie 52, de sorte qu'elle s'exerce sur toute la section S de cette deuxième partie 52. Cette pression peut donc faire reculer cette deuxième partie 52 en même temps que la première partie 50, procurant ainsi la réaction voulue sur la tige de commande.When braking under normal conditions, the pressure in the interior volume V of the master cylinder is exerted on the one hand in the annular reaction chamber 35 by the channel 78 and the grooves 76 and 72, and on the other hand on the axial extension 70 of the second part 52, so that it is exerted on all the section S of this second part 52. This pressure can so roll back this second part 52 at the same time as the first part 50, providing thus the desired reaction on the control rod.

Lors d'un freinage d'urgence, la tige de poussée 42 fait avancer la seconde partie 52. Le prolongement axial plein 70 coulisse alors dans l'ouverture 36 jusqu'à ce que le joint à lèvre 74 quitte la gorge annulaire 76 et assure une étanchéité parfaite entre les première et deuxième parties 50 et 52. Un mouvement supplémentaire vers l'avant de la deuxième partie 52 est permis grâce au joint à lèvre 74, jouant le rôle d'un clapet anti-retour, et autorisant la circulation de fluide de la chambre de réaction 35 vers le canal 78 et vers le volume intérieur V du maítre-cylindre.During emergency braking, the push rod 42 advances the second part 52. The extension full axial 70 then slides in the opening 36 until the lip seal 74 leaves the annular groove 76 and ensures a perfect seal between the first and second parts 50 and 52. Additional forward movement of the second part 52 is permitted thanks to lip seal 74, playing the role of a non-return valve, and allowing circulation of fluid from the reaction chamber 35 to the channel 78 and to the interior volume V of the master cylinder.

La communication de fluide du volume V du maítre-cylindre vers la chambre de reaction annulaire 35 étant alors interrompue par le joint à lèvre 74, interdisant cette communication, la pression régnant à l'intérieur du maítre-cylindre ne s'exerce plus alors que sur la section S2 de la deuxième partie 52 définie par le diamètre externe du prolongement axial 70. La pression communiquée par le canal 78 à la gorge 72 s'exerce sur les côtes avant et arrière de cette gorge, et elle est donc sans effet sur la deuxième partie 52.The communication of fluid from volume V of the master cylinder to the annular reaction chamber 35 is then interrupted by the lip seal 74, preventing this communication, the pressure prevailing inside the master cylinder no longer exerts while on the section S 2 of the second part 52 defined by the external diameter of the axial extension 70. The pressure communicated by the channel 78 to the groove 72 is exerted on the front and rear ribs of this groove, and it is therefore without effect on the second part 52.

Lorsque le conducteur relâche son effort, la pression baisse dans le volume interieur V du maítre-cylindre. Du fait de cette baisse de pression, et de l'étanchéité non parfaite entre le prolongement 70 et l'ouverture 36, la deuxième partie 52 peut reculer suffisamment pour ramener le joint à lèvre 74 dans la gorge 76 du cylindre mobile 32, et ainsi permettre la communication entre la chambre de réaction 35 et le volume intérieur V du maítre-cylindre. La deuxième partie 52 peut alors reculer sous l'action du ressort 54, et les différentes pièces mobiles reprennent alors leur position de repos illustrée sur la Figure 6.When the driver releases his effort, the pressure drops in the interior volume V of the master cylinder. Due to this drop in pressure, and the non-perfect seal between the extension 70 and the opening 36, the second part 52 can move back enough to bring the lip seal 74 in groove 76 of movable cylinder 32, and thus allow communication between the reaction chamber 35 and the interior volume V of the master cylinder. The second part 52 can then move back under the action of the spring 54, and the various moving parts resume then their rest position illustrated in Figure 6.

La variante de réalisation représentée sur la Figure constitue en fait une variante de réalisation du mode de réalisation représenté sur la Figure 4. Selon cette dernière variante, la première partie 50 est en butée vers l'avant sur le fond du cylindre mobile 32, et elle est percée d'un alésage axial 62 dans lequel est susceptible de coulisser de façon étanche la deuxième partie 52 grâce à un joint annulaire 63.The variant embodiment shown in the Figure in fact constitutes an alternative embodiment of the embodiment shown in Figure 4. According to this latter variant, the first part 50 is in abutment forward on the bottom of the movable cylinder 32, and it is pierced an axial bore 62 in which the second is capable of sliding in leaktight fashion part 52 thanks to an annular seal 63.

La deuxième partie 52 est de forme générale cylindrique, solidaire à son extrémité avant d'un disque 80, de diamètre exterieur superieur à celui de l'alésage 62.The second part 52 is of generally cylindrical shape, integral at its front end with a disc 80, with an outside diameter greater than that of bore 62.

Selon cette variante, une troisième partie 82 est constituée d'un piston 82 susceptible de coulisser de façon étanche grâce à un joint annulaire 83 dans un alésage 84 du cylindre mobile 32. Cette troisième partie 82 est sollicitée vers l'arrière en position de repos par un ressort 86 de façon à venir en butée arrière, au repos, sur la première partie 50, par l'intermédiaire de dents ou de créneaux 88.According to this variant, a third part 82 consists of a piston 82 capable of sliding tightly thanks to an annular seal 83 in a bore 84 of the movable cylinder 32. This third part 82 is biased towards the rear in the rest position by a spring 86 of so as to come into abutment, at rest, on the first part 50, by means of teeth or slots 88.

Cette troisième partie 82 est formée avec une ouverture centrale traversante 90, étagée de façon à ménager un épaulement sur lequel vient en appui un ressort 92, par ailleurs en appui sur le disque 80 de la deuxième partie 52.This third part 82 is formed with a through central opening 90, stepped so to provide a shoulder on which a spring 92 bears, also bearing on the disc 80 of the second part 52.

La précontrainte au repos du ressort 86 est inférieure à celle du ressort 46, et la somme des précontraintes au repos des ressorts 86 et 92 est inférieure à celle du ressort 46, de façon à ce que la deuxième partie soit, au repos, en butée avant sur le cylindre mobile 32. De plus, le ressort 92 a une raideur inférieure a celle du ressort 86.The spring preload at rest is less than that of spring 46, and the sum of the prestressed at rest of the springs 86 and 92 is less than that of the spring 46, so that that the second part is, at rest, in front stop on the movable cylinder 32. In addition, the spring 92 has a lower stiffness than that of spring 86.

Selon cette variante l'organe d'obturation de la chambre de réaction 35 est constitué d'un joint annulaire 94, dispose sur la deuxième partie 52 où, comme on la représente, sur la troisième partie 82, autour de l'extrémité arrière de l'ouverture 90.According to this variant, the shutter member of the reaction chamber 35 consists of a annular seal 94, has on the second part 52 where, as shown, on the third part 82, around the rear end of the opening 90.

En fonctionnement, lors d'un freinage dans des conditions normales, la pression régnant dans le volume intérieur V du maítre-cylindre est communiquée à la chambre de reaction 35 par l'ouverture 90, pour s'exercer sur la section S de la première partie 50, et la faire reculer en même temps que la deuxième partie 52 grâce à l'étanchéité du joint annulaire 63.In operation, when braking under normal conditions, the pressure prevailing in the internal volume V of the master cylinder is communicated to the reaction chamber 35 by the opening 90, to be exerted on the section S of the first part 50, and to make it move back in same time as the second part 52 thanks to the sealing of the annular seal 63.

Lors d'un freinage d'urgence, la tige de poussée 42 fait avancer la seconde partie 52, qui coulisse alors dans l'alésage 62. La raideur du ressort 86 étant supérieure à celle du ressort 92, ce dernier se comprime le premier et permet à la deuxième partie de venir au contact de la troisième partie, ou plus exactement du joint annulaire 94. Ce faisant, la communication entre le volume V du maítre-cylindre et la chambre de reaction 35 est interrompue. Le mouvement vers l'avant de l'ensemble deuxième partie/troisième partie n'est pas limité puisque cet ensemble se déplace dans la chambre de réaction qui a alors un volume constant.During emergency braking, the push rod 42 advances the second part 52, which slides then in the bore 62. The stiffness of the spring 86 being greater than that of the spring 92, this last compresses the first and allows the second part to come into contact with the third part, or more exactly of the annular seal 94. In doing so, the communication between the volume V of the master cylinder and the reaction chamber 35 is interrupted. The movement towards the front of the second part / third part set is not limited since this set is moves in the reaction chamber which then has a constant volume.

La chambre de réaction 35 étant isolée du volume intérieur V du maítre-cylindre, la pression régnant à l'intérieur du maítre-cylindre ne s'exerce plus alors que sur la section S2 de la deuxième partie 52 définie par le diamètre intérieur du joint annulaire 94.The reaction chamber 35 being isolated from the internal volume V of the master cylinder, the pressure prevailing inside the master cylinder no longer exerts itself only on the section S 2 of the second part 52 defined by the internal diameter of the ring seal 94.

Lorsque le conducteur relâche son effort, comme dans les modes de réalisation précédent, le recul de la cloison mobile 16 et du cylindre mobile 32 a pour effet de faire baisser la pression dans le volume intérieur V du maítre-cylindre.When the driver releases his effort, as in the previous embodiments, the retraction of the movable partition 16 and of the movable cylinder 32 has the effect of reducing the pressure in the interior volume V of the master cylinder.

Simultanément, la tige de poussée 42 ayant reculé, le ressort 86 peut repousser la troisième partie 82 vers l'arrière, jusqu'à ce qu'elle vienne en butée sur la première partie 50, tandis que le ressort 92 peut repousser la deuxième partie 52 jusqu'à ce qu'elle vienne également en butée sur la première partie 50.Simultaneously, the push rod 42 having retreated, the spring 86 can push back the third part 82 backwards, until it comes to a stop on the first part 50, while the spring 92 can push back the second part 52 until it also comes into abutment on the first part 50.

Les différentes pièces mobiles reprennent alors leur position de repos illustrée sur la Figure 7, et la chambre de réaction 35 est à nouveau en communication avec le volume intérieur du maítre-cylindre.The different moving parts then resume their rest position illustrated in FIG. 7, and the reaction chamber 35 is again in communication with the interior volume of the master cylinder.

On voit donc bien que les différentes variantes de réalisation que l'on vient d'exposer permettent d'obtenir les mêmes avantages que le premier mode de réalisation, à savoir des caractéristiques de fonctionnement améliorées en cas de freinage d'urgence. Chaque mode de réalisation présente ainsi un rapport d'assistance nettement supérieur à celui qu'a présenté dans des conditions normales de fonctionnement. Le changement de rapport d'assistance est obtenu automatiquement par la simple exploitation du mouvement relatif entre le plongeur 28 et le piston pneumatique 22. Les différents moyens utilisés pour obtenir ce resultat sont relativement simples, et sont donc de coût réduit et de fonctionnement fiable en toutes circonstances, aussi bien dans des conditions normales de fonctionnement que dans des conditions d'urgence.It is therefore clear that the different variants which we have just described allow obtain the same advantages as the first embodiment, namely characteristics improved operation in case of emergency braking. Each embodiment thus presents a significantly better assistance report than that presented under conditions normal operating conditions. The change of assistance report is obtained automatically by the simple exploitation of the relative movement between the plunger 28 and the piston pneumatic 22. The various means used to obtain this result are relatively simple, and therefore are of low cost and reliable operation under all circumstances, as well under normal operating conditions as under emergency conditions.

Bien entendu, l'homme de l'art pourra apporter diverses modifications aux différents modes de réalisation qui ont été exposés, sans pour autant sortir du cadre ce l'invention telle que definie par les revendications annexées.Of course, those skilled in the art can make various modifications to the different modes of realization which have been exposed, without departing from the scope of this invention as defined by the appended claims.

Claims (14)

  1. Boosted braking device for a motor vehicle, comprising on the one hand a master cylinder (200) filled with a brake fluid and equipped with a main hydraulic piston (30) intended to receive an actuating force composed of an input force and of a boost force both acting in an axial direction, and on the other hand a pneumatic booster (100) which can be operated by applying the input force to an operating rod (26) secured to a plunger (28) controlling the opening of a three-way valve (24), so as to exert the actuating force on the main hydraulic piston (30), the booster including a rigid casing (10) divided in leaktight fashion into at least two chambers (12, 14) by means of at least one moving partition (16) which can be acted upon via a difference in pressure between the two chambers (12, 14) resulting from the opening of the three-way valve (24) and of driving along a pneumatic piston (22) which can move with respect to the casing (10), bearing the three-way valve (24) and contributing at least to transmitting the boost force, the main hydraulic piston (30) of the master cylinder (200) itself including a hollow moving cylinder (32) communicating with the interior volume (V) of the master cylinder, receiving at least part of the boost force, and inside which there slides, in leaktight fashion and in the axial direction, a secondary hydraulic piston (34) capable of receiving at least the input force, first elastic means (46) exerting a first elastic force between the secondary hydraulic piston (34) and the moving cylinder (32) and urging the secondary hydraulic piston (34) in the direction of the master cylinder (200), at least one opening (36) being made in the moving cylinder (32) in order to make the interior (35) of the latter communicate with the interior (V) of the master cylinder, the secondary hydraulic piston (34) including a two-way valve means (56, 58, 66, 74, 94) between the interior volume (V) of the master cylinder and the interior (35) of the moving cylinder (32), characterized in that the secondary hydraulic piston (34) is composite and includes a first part (50) which, in the position of rest, is in abutment against the moving cylinder (32) under the effect of the first elastic means (46), and a second part (52) capable of sliding with respect to the first part (50), in that second elastic means (54, 92) exert a second elastic force backwards on the second part (52) in order to urge it into abutment, in the position of rest, against the first part (50), in that the two-way valve means, which is normally open, is formed by the second part (52) of the secondary hydraulic piston and the main hydraulic piston (30), or by the second part (52) of the secondary hydraulic piston and a third part (82) borne by the main hydraulic piston, and in that a movement of the second part (52) of the secondary hydraulic piston towards the master cylinder (200) with respect to the main hydraulic piston, or with respect to the third part borne by the main hydraulic piston causes the two-way valve means (56, 58, 66, 74, 94) to close and interrupts the communication between the interior volume (v) of the master cylinder and the interior (35) of the moving cylinder (32).
  2. Boosted braking device according to Claim 1, characterized in that the plunger (28) is secured to a push rod (42) actuating the two-way valve means (56, 58, 66, 74, 94) in the direction of closure upon a relative movement between the plunger (28) and the moving partition (16) corresponding to a variation greater than a predetermined value in the input force.
  3. Boosted braking device according to Claim 2, characterized in that the two-way valve means (56) consists of an annular seal (56) 'arranged on a front face of the second part (52) facing the opening (36) made in the moving cylinder (32) or on the moving cylinder (32) at the edge of the opening (36) made therein.
  4. Boosted braking device according to Claim 2, characterized in that the two-way valve means (58) is formed of a hollow axial extension (58) of the second part (52), extending forwards, and capable of sliding in almost leaktight fashion in the opening (36) made in the moving cylinder (32) and equipped at its rear part with at least one opening (60).
  5. Boosted braking device according to Claim 2, characterized in that the second part (52) is capable of sliding in leaktight fashion in the first part (50), and in that the two-way valve means (58) is formed by a hollow axial extension (58) of the second part (52), extending forwards, sliding in almost leaktight fashion in the opening (36) made in the moving cylinder (32) and equipped at its rear part with at least one opening (60).
  6. Boosted braking device according to Claim 2, characterized in that the second part (52) is formed with a hollow axial extension (58), equipped at its rear part with at least one opening (60), in that the two-way valve means (66) is formed by at least one channel (68) provided on the outside periphery and along part of the length of the hollow axial extension (58) and which interacts selectively with an axial bore (36) of the moving cylinder (32), and in that the hollow axial extension (58) contains a non-return valve (66) allowing fluid to pass from the interior (35) of the moving cylinder (32) towards the interior volume (V) of the master cylinder (200) and preventing fluid from passing in the other direction.
  7. Boosted braking device according to Claim 2, characterized in that the second part (52) is formed with a solid axial extension (70) capable of sliding in almost leaktight fashion in the opening (36) made in the moving cylinder (32), and with a peripheral groove (72), the two-way valve means (74) being formed by a lip seal (74) arranged in this peripheral groove (72), the moving cylinder (32) being formed with an annular groove (76) communicating with the interior volume (V) of the master cylinder via a channel (78) formed in the moving cylinder (32), the peripheral grooves (72) and the annular grooves. (76) lying substantially opposite one another in the position of rest.
  8. Boosted braking device according to Claim 2, characterized in that the second part (52) can slide in leaktight fashion in the first part (50), and in that a third part (82) is capable of sliding in leaktight fashion in the moving cylinder (32), the third part (82) being urged backwards by third elastic means (86) so that in the position of rest they come into abutment on the first part (50), the second elastic means (92) being arranged between the second part (52) and the third part (82), the third part (82) being formed with a central opening (90) making the interior (35) of the moving cylinder (32) communicate with the interior volume of the master cylinder (200), the two-way valve means (94) being formed by an annular seal (94) arranged on the second part (52) or on the third part (82).
  9. Boosted braking device according to one of Claims 3 to 8, characterized in that the pressure of the brake fluid in the interior volume (V) of the master cylinder (200) is applied to a first cross-section (S) of the hollow moving cylinder (32) when the two-way valve means (56, 58, 66, 74, 94) is open, and to a second cross-section (S2) of the secondary hydraulic piston (34), this cross-section being smaller than the first cross-section (S), when the two-way valve means (56, 58, 66, 74, 92) is closed.
  10. Boosted braking device according to Claims 3 and 9, characterized in that the second cross-section (S2) is defined by the inside diameter of the annular seal (56) on the front face of the second part (52) or on the moving cylinder (32) at the edge of the opening (36) made therein.
  11. Boosted braking device according to one of Claims 4 to 7 and Claim 9, characterized in that the second cross-section (S2) is defined by the outside diameter of the axial extension (58, 70) of the second part (52).
  12. Boosted braking device according to Claims 8 and 9, characterized in that the second cross-section (S2) is defined by the inside diameter of the annular seal (94) arranged on the second part (52) or on the third part (82).
  13. Boosted braking device according to any one of the preceding claims, characterized in that a buffer piece (45) made of elastomeric material is arranged at the rear of the second part (52) and/or at the front of the plunger (28).
  14. Method of implementing the boosted braking device according to any one of the preceding claims, characterized in that the predetermined value for the variation in the input force is predetermined so as to correspond to a braking action under emergency conditions.
EP97924090A 1996-07-23 1997-05-14 Power-assisted braking device with a variable assistance ratio Expired - Lifetime EP0912382B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR9609242 1996-07-23
FR9609242A FR2751602B1 (en) 1996-07-23 1996-07-23 ASSISTED BRAKING DEVICE WITH VARIABLE ASSISTANCE RATIO
PCT/FR1997/000852 WO1998003385A1 (en) 1996-07-23 1997-05-14 Power-assisted braking device with a variable assistance ratio

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EP0912382A1 EP0912382A1 (en) 1999-05-06
EP0912382B1 true EP0912382B1 (en) 2002-06-12

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EP (1) EP0912382B1 (en)
JP (1) JP2000514746A (en)
KR (1) KR20000065255A (en)
CN (1) CN1087244C (en)
AR (1) AR007182A1 (en)
BR (1) BR9710395A (en)
DE (1) DE69713328T2 (en)
ES (1) ES2177981T3 (en)
FR (1) FR2751602B1 (en)
PL (1) PL184079B1 (en)
RU (1) RU2175924C2 (en)
TR (1) TR199900085T2 (en)
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WO (1) WO1998003385A1 (en)

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CN1223619A (en) 1999-07-21
AU718664B2 (en) 2000-04-20
WO1998003385A1 (en) 1998-01-29
TR199900085T2 (en) 1999-04-21
AU2967097A (en) 1998-02-10
FR2751602B1 (en) 1998-09-18
TW348135B (en) 1998-12-21
BR9710395A (en) 1999-08-17
ES2177981T3 (en) 2002-12-16
RU2175924C2 (en) 2001-11-20
PL184079B1 (en) 2002-08-30
EP0912382A1 (en) 1999-05-06
KR20000065255A (en) 2000-11-06
JP2000514746A (en) 2000-11-07
DE69713328D1 (en) 2002-07-18
PL331342A1 (en) 1999-07-05
DE69713328T2 (en) 2003-01-02
FR2751602A1 (en) 1998-01-30
CN1087244C (en) 2002-07-10
AR007182A1 (en) 1999-10-13
US5921084A (en) 1999-07-13

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